阅读说明：本技术 线性压缩机 (Linear compressor ) 是由 裵相恩 李尚旻 金贤洙 河东均 于 2021-05-12 设计创作，主要内容包括：根据本实施例的线性压缩机,其包括：弹簧支撑件,其与活塞或所述马达的可动子结合并进行往复运动；共振弹簧,其支撑于所述弹簧支撑件,并将所述活塞支撑为进行共振运动；以及弹簧盖,所述共振弹簧的端部插入到弹簧盖并被支撑,所述弹簧盖可以包括：消音空间部,其具有预设的体积,并与所述外壳的内部空间隔开；以及消音通道部,其贯通所述消音空间部的轴向的侧面,使得所述消音空间部与所述外壳的内部空间连通。由此,在不追加设置额外的消音器的情况下,也能有效地抵消在外壳的内部中所产生的噪音。(The linear compressor according to the present embodiment includes: a spring supporter coupled to the piston or the mover of the motor and reciprocating; a resonant spring supported by the spring support and supporting the piston to perform a resonant motion; and a spring cover to which an end of the resonant spring is inserted and supported, the spring cover may include: a sound deadening space part having a predetermined volume and spaced apart from an inner space of the case; and a silencing passage part penetrating through an axial side surface of the silencing space part so that the silencing space part is communicated with an inner space of the housing. Thus, the noise generated in the interior of the housing can be effectively offset without additionally providing an additional muffler.)

1. A linear compressor, comprising:

a housing having a sealed inner space;

a motor provided in the inner space of the housing and configured to reciprocate the mover;

a piston coupled to a movable element of the motor and reciprocating in the cylinder;

a spring supporting the piston in an axial direction such that the piston performs a resonant motion; and

a spring cover in which an end of the spring is inserted and supported;

the spring cover includes:

a space part having a prescribed volume and spaced apart from an inner space of the housing; and

and a passage portion that penetrates through an axial side surface of the space portion so that the space portion communicates with an internal space of the housing.

2. The linear compressor of claim 1,

further comprising a spring support coupled to the piston or the mover of the motor and reciprocating,

a cover support hole is formed in the spring support, and the spring cover is inserted into and coupled to the cover support hole of the spring support.

3. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes first and second covers respectively inserted into both axial sides of the cover support hole,

the first cover and the second cover communicate with each other by being inserted into cover support holes provided to the spring support to form the space portion inside the first cover and the second cover.

4. The linear compressor of claim 1,

further comprising a spring support coupled to the piston or the mover of the motor and reciprocating,

an axial length of the space portion is formed to be greater than an axial length of a cover support hole provided to the spring supporter to insert the spring cover.

5. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes first and second covers respectively inserted into both axial sides of the cover support hole,

the volume of the first space portion formed inside the first cover is formed to be the same as the volume of the second space portion formed inside the second cover.

6. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes first and second covers respectively inserted into both axial sides of the cover support hole,

the volume of the first space portion formed inside the first cover is formed to be different from the volume of the second space portion formed inside the second cover.

7. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes first and second covers respectively inserted into both axial sides of the cover support hole,

the channel portion is formed through at least one of the first cover and the second cover.

8. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes first and second covers respectively inserted into both axial sides of the cover support hole,

the axial side surface of any one of the first cover and the second cover is blocked, and at least a part of the axial side surface of the opposite cover is opened to form the channel portion.

9. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes first and second covers respectively inserted into both axial sides of the cover support hole,

the passage portion includes:

a first channel part disposed on one surface of the first cover; and

and a second channel part disposed on one surface of the second cover.

10. The linear compressor of claim 1,

the channel part comprises a first channel part and a second channel part which are respectively arranged at two axial sides of the spring cover,

the first passage portion is formed to have a sectional area or length different from that of the second passage portion.

11. The linear compressor of claim 1,

the channel part comprises a first channel part and a second channel part which are respectively arranged at two axial sides of the spring cover,

the first channel portion and the second channel portion are formed to extend along different lines from each other in the axial direction.

12. The linear compressor of claim 1,

the channel portion extends a predetermined length from one surface of the spring cover.

13. The linear compressor of claim 1,

the spring cover is provided with a plurality of springs along the circumferential direction,

the plurality of spring covers respectively include the space portion and the passage portion.

14. The linear compressor of claim 1,

the spring cover is provided with a plurality of springs along the circumferential direction,

the respective space portions and the channel portions of the plurality of spring covers are formed to have the same specification.

15. The linear compressor of claim 1,

the spring cover is provided with a plurality of springs along the circumferential direction,

in the plurality of spring covers, at least a part of the space portion and the passage portion of the spring cover are formed to have different specifications.

16. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes:

a first cover coupled to one side surface of the spring support in an axial direction; and

a second cover coupled to the other axial side surface of the spring support,

the first cover includes:

a first hole insertion part inserted from a first side surface of the spring supporter to one side of the cover support hole;

a first cover support portion extending in a flange shape from an outer peripheral surface of the first hole insertion portion and supported to a first side surface of the spring support in an axial direction; and

a first spring insertion portion extending from the first cover support portion toward an opposite side of the first hole insertion portion,

the second cover includes:

a second hole insertion part inserted from a second side of the spring supporter to the other side of the cover support hole;

a second cover support portion extending in a flange shape from an outer circumferential surface of the second hole insertion portion and supported to a second side surface of the spring support in an axial direction; and

a second spring insertion portion extending from the second cover support portion toward an opposite side of the second hole insertion portion;

an end of the first hole insertion portion and an end of the second hole insertion portion are opposed to each other and opened in such a manner as to communicate with each other to form the space portion,

at least a part of either one of the side surfaces of the first spring insertion portion and the second spring insertion portion in the axial direction is opened to form the passage portion.

17. The linear compressor of claim 1,

further comprises a spring support coupled to the piston or the movable element of the motor and having a cover support hole,

the spring cover includes:

a first cover coupled to one side surface of the spring support in an axial direction; and

a second cover coupled to the other axial side surface of the spring support,

the first cover includes:

a hole penetration portion inserted into the cover support hole from a first side surface of the spring supporter;

a first cover support portion extending in a flange shape from an outer peripheral surface of the hole penetration portion and supported by a first side surface of the spring support in an axial direction; and

a first spring insertion portion extending from the first cover support portion toward an opposite side of the hole penetration portion;

the second cover includes:

a cover coupling part coupled to the hole penetration part;

a second cover supporting portion extending in a flange shape from an outer circumferential surface of the cover coupling portion and supported to a second side surface of the spring support in an axial direction; and

a second spring insertion portion extending from the cover coupling portion toward an opposite side of the first spring insertion portion;

the hole penetration portion is inserted into the cover support hole along the axial direction,

the cover coupling portion is inserted from the other side of the spring supporter and coupled to the hole penetration portion.

18. The linear compressor of claim 1,

further comprising a spring support coupled to the piston or the mover of the motor,

the spring cover includes:

a first cover coupled to one side surface of the spring support in an axial direction and including a first spring insertion portion; and

a second cover coupled to the other axial side surface of the spring support and having a second spring insertion portion,

in the first spring insertion portion and the second spring insertion portion, a cross-sectional area of an inner peripheral surface of at least one of the spring insertion portions is formed to have the same inner diameter along an axial direction.

19. The linear compressor of claim 1,

further comprising a spring support coupled to the piston or the mover of the motor,

the spring cover includes:

a first cover coupled to one side surface of the spring support in an axial direction and including a first spring insertion portion; and

a second cover coupled to the other axial side surface of the spring support and having a second spring insertion portion,

in the first spring insertion portion and the second spring insertion portion, a cross-sectional area of an inner peripheral surface of at least one of the spring insertion portions is formed to become smaller as it becomes farther from the spring support along the axial direction.

20. The linear compressor of claim 1,

further comprising a spring support coupled to the piston or the mover of the motor and reciprocating,

the spring cover penetrates from one axial side surface of the spring support to the other axial side surface of the spring support and is combined with the spring cover,

a part of at least any one of the two side surfaces in the axial direction of the spring cover is opened to form the passage portion.

21. The linear compressor of any one of claims 1 to 20,

a stator cover and a rear cover are respectively arranged on one side of the motor, the stator cover and the rear cover respectively support two ends of the spring,

the spring cover is arranged on the stator cover or the rear cover.

22. The linear compressor of any one of claims 1 to 20,

the spring is divided into a front side spring and a rear side spring in the axial direction,

both end portions of the spring cover are respectively inserted between the front side spring and the rear side spring so that the front side spring and the rear side spring are connected.

Technical Field

The invention relates to a linear compressor, in particular to a silencing device.

Background

In the linear compressor, a linear motor is provided inside a sealed casing (shell), and a piston connected to the linear motor sucks and compresses a refrigerant while performing a reciprocating linear motion inside a cylinder tube, and then discharges the refrigerant.

Like other compressors, such a linear compressor generates vibration noise (hereinafter, simply referred to as noise) when the compressor is operated. Such noise is transmitted to the outside through the outer case, thereby aggravating noise of a product (e.g., a refrigerator) provided with the linear compressor.

Therefore, the conventional linear compressor is provided with a structure for suppressing or reducing compressor noise. For example, as in patent document 1 (Korean laid-open patent publication: KR 10-2016-.

However, even if the suction muffler or the discharge cover is provided, noise that cannot be cancelled may occur. For example, there is a limit in effectively attenuating noise in the 800Hz band (see fig. 10).

In view of this, an additional muffler may be additionally provided inside the housing. However, as the number of individual parts increases, not only may the material cost increase, but also the number of assembly processes increases due to the increase in the number of parts, thereby possibly increasing the overall manufacturing cost of the compressor.

In addition, in the case where an additional muffler is installed inside the casing, since the internal volume of the casing needs to be increased, the size of the compressor as a whole may be increased or heavy.

Further, in order to cancel noise in various frequency bands generated inside the housing, it is necessary to provide various predetermined mufflers, and therefore the above-described problems may occur in combination.

Disclosure of Invention

An object of the present invention is to provide a linear compressor capable of effectively canceling noise generated in the interior of a casing.

Another object of the present invention is to provide a linear compressor capable of canceling noise generated in the interior of a casing by using an existing member without additionally providing a muffler in the interior of the casing.

Another object of the present invention is to provide a linear compressor capable of effectively canceling various frequency band noises generated in the interior of a casing.

In order to achieve the object of the present invention, a piston is combined to a mover of the linear motor, and a compression coil spring may be elastically supported at one side of the piston in a reciprocating direction. A spring cap (spring cap) may be provided, which may be inserted into an end of the compression coil spring to restrain a fixing position of the compression coil spring. A sound deadening space may be formed inside the spring cover.

Thus, even when the muffler is not additionally provided in the housing, the noise generated in the housing can be effectively cancelled.

Here, the plurality of compression coil springs may be arranged in the axial direction, and the spring cover may be provided between the plurality of compression coil springs. Thus, noise generated in the housing interior can be effectively cancelled out in the expansion and contraction process of the compression coil spring.

Further, between the plurality of compression coil springs, a spring supporter (supporter) coupled with the piston may be provided. The spring covers may be respectively insert-coupled to the spring supporter from both axial sides of the spring supporter. The opposite faces of the both side spring covers combined at both sides of the spring supporter are opened so that the sound deadening space can be formed. A through hole may be formed in one side of the both side spring covers in an axial direction to communicate with the sound deadening space. Thus, the muffler can be configured by using existing components without providing an additional muffler inside the housing.

Specifically, the linear compressor according to the present invention may include: a housing having a sealed interior space; a motor provided in the inner space of the housing and configured to reciprocate the mover; a piston coupled to a movable element of the motor and reciprocating in the cylinder; a spring supporting the piston in an axial direction such that the piston performs a resonant motion; and a spring cover to which an end of the spring is inserted and supported. The spring cover may include: a space part having a prescribed volume and spaced apart from an inner space of the housing; and a passage portion that penetrates through an axial side surface of the space portion so that the space portion communicates with an internal space of the housing. Thus, the noise generated in the interior of the housing can be effectively cancelled by the existing member.

As an example, the piston may further include a spring supporter coupled to the piston or the mover of the motor to reciprocate, and a cover support hole may be formed in the spring supporter, and the spring cover may be inserted into and coupled to the cover support hole of the spring supporter. Thus, the muffler can be configured by using existing components without additionally providing the muffler inside the housing.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole. The spring cover may include first and second covers respectively inserted at both axial sides of the cover support hole. The first cover and the second cover communicate with each other by being inserted into cover support holes provided to the spring support so that the space portion can be formed inside the first cover and the second cover. Thus, the muffler using the spring cover can be easily formed.

As another example, a spring support may be further included, and the spring support may be coupled to the piston or the mover of the motor. An axial length of the space portion may be formed to be greater than an axial length of a cover support hole provided to the spring supporter to insert the spring cover. This ensures a wider sound deadening space.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole. The spring cover may include first and second covers respectively inserted at both axial sides of the cover support hole. The volume of the first space portion formed inside the first cover may be formed to be the same as the volume of the second space portion formed inside the second cover.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole, and the spring cover may include a first cover and a second cover respectively inserted at both axial sides of the cover support hole. The volume of the first space portion formed inside the first cover may be formed to be greater than or less than the volume of the second space portion formed inside the second cover.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole. The spring cover may include first and second covers respectively inserted at both axial sides of the cover support hole. The channel portion may be formed to penetrate at least one of the first cover and the second cover. This makes it possible to easily form a Helmholtz (Helmholtz) silencer.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole. The spring cover may include first and second covers respectively inserted at both axial sides of the cover support hole. The channel portion may be formed by one of a surface of the first cover and a surface of the second cover being closed and at least a portion of the surface of the opposite side being open.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole. The spring cover may include first and second covers respectively inserted at both axial sides of the cover support hole. The channel part may include: a first channel part disposed on one surface of the first cover; and a second channel portion provided on one surface of the second cover. This makes it possible to attenuate noise while reciprocating on both sides, and accordingly, the noise attenuation effect can be improved.

As another example, the passage portion may include a first passage portion and a second passage portion that are respectively provided at both sides of the spring cover in the axial direction. The first passage portion may be formed to have a sectional area or length different from that of the second passage portion. This makes it possible to cancel noise at various frequencies.

As another example, the passage portion may include a first passage portion and a second passage portion that are respectively provided at both sides of the spring cover in the axial direction. The first channel portion and the second channel portion may be formed so as to be located on different lines from each other in the axial direction. Thus, even when the silencing space is opened in two directions, the noise attenuation effect can be improved.

As another example, the channel portion may extend a predetermined length from one surface of the spring cover. This can further improve the noise attenuation effect.

As another example, the plurality of spring caps may be provided along a circumferential direction, and the space portion and the passage portion may be formed in each of the plurality of spring caps. Thus, a plurality of noise reduction space portions are formed, and the noise attenuation effect can be improved.

As another example, the plurality of spring caps may be provided along a circumferential direction, and the space portion and the passage portion of each of the plurality of spring caps may be formed to have the same specification.

As another example, at least a part of the spring cover of the plurality of spring covers may have a silencing space and a silencing passage formed therein with different specifications. This can attenuate noise at various frequencies.

As another example, a spring support may be further included, and the spring support may be coupled to the piston or the mover of the motor. The spring cover may include: a first cover coupled to one side surface of the spring support in an axial direction; and a second cover coupled to the other side surface of the spring supporter in the axial direction. The first cover may include: a first hole insertion part inserted from a first side surface of the spring supporter; a first cover support portion extending in a flange shape from an outer peripheral surface of the first hole insertion portion and supported to a first side surface of the spring support in an axial direction; and a first spring insertion portion extending from the first cover support portion toward an opposite side of the first hole insertion portion. The second cover may include: a second hole insertion part inserted from a second side of the spring supporter; a second cover support portion extending in a flange shape from an outer peripheral surface of the second hole insertion portion and supported to a second side surface of the spring support in an axial direction; and a second spring insertion portion extending from the second cover support portion toward an opposite side of the second hole insertion portion. An end portion of the first hole insertion portion and an end portion of the second hole insertion portion opposite to the end portion are opened to communicate with each other, thereby forming the space portion, and at least a part of either one of an axial side surface of the first spring insertion portion and an axial side surface of the second spring insertion portion is opened, thereby forming the passage portion.

As another example, a spring support may be further included, the spring support being coupled with the piston or the mover of the motor and having a cover support hole. The spring cover may include: a first cover coupled to one side surface of the spring support in an axial direction; and a second cover coupled to the other side surface of the spring supporter in the axial direction. The first cover may include: a hole penetration portion inserted into the cover support hole from a first side surface of the spring supporter; a first cover support portion extending in a flange shape from an outer peripheral surface of the hole penetration portion and supported by a first side surface of the spring support in an axial direction; and a first spring insertion portion extending from the first cover support portion toward an opposite side of the hole penetration portion. The second cover may include: a cover coupling portion coupled to the hole penetration portion; a second cover support portion extending in a flange shape from an outer peripheral surface of the cover coupling portion and supported to a second side surface of the spring support member in an axial direction; a second spring insertion portion extending from the cover coupling portion toward an opposite side to the first spring insertion portion. The hole penetration portion is inserted into and coupled to the cover support hole so as to penetrate the cover support hole in an axial direction, and the cover coupling portion may be inserted into and coupled to the hole penetration portion from the other side of the spring supporter.

As another example, a spring support may be further included, and the spring support may be coupled to the piston or the mover of the motor. The spring cover may include: a first cover coupled to one side surface of the spring support in an axial direction and having a first spring insertion portion; and a second cover coupled to the other side surface of the spring supporter in the axial direction and having a second spring insertion portion. In the first spring insertion portion and the second spring insertion portion, a cross-sectional area of an inner peripheral surface of at least one of the spring insertion portions may be formed to have the same inner diameter in an axial direction.

As another example, a spring support may be further included, and the spring support may be coupled to the piston or the mover of the motor. The spring cover may include: a first cover coupled to one side surface of the spring support in an axial direction and having a first spring insertion portion; and a second cover coupled to the other side surface of the spring supporter in the axial direction and having a second spring insertion portion. In the first spring insertion portion and the second spring insertion portion, a cross-sectional area of an inner peripheral surface of at least one of the spring insertion portions may be formed to become smaller as it becomes farther from the spring holder in an axial direction.

As another example, a spring support may be further included, and the spring support may be coupled to the piston or the mover of the motor. The spring cover is coupled to the spring support member so as to penetrate from one axial side surface of the spring support member toward the other axial side surface, and the passage portion may be formed by forming an opening in a part of at least one of the two axial side surfaces of the spring cover.

As another example, a stator cover (cover) and a rear cover (rear cover) that can support both ends of the spring may be provided at one side of the motor, and the spring cover may be provided at the stator cover or the rear cover.

As another example, the spring may be divided into a front side spring and a rear side spring in an axial direction, and both end portions of the spring cover may be respectively inserted between the front side spring and the rear side spring so as to connect the front side spring and the rear side spring to each other.

Drawings

Fig. 1 is a perspective view of the external appearance of the linear compressor of the present embodiment as viewed from the suction side.

Fig. 2 is a sectional view taken along line iv-iv of fig. 1, which is a sectional view showing the interior of the linear compressor of the present embodiment.

Fig. 3 is a perspective view of the compressor body of fig. 1 as viewed from the rear side.

Fig. 4 is a perspective view illustrating the resonance unit of fig. 3 in an exploded view.

Fig. 5A is a plan view showing a spring supporter to which spring caps of the same specification are mounted, and fig. 5B to 5D are sectional views of V-V, V '-V', V "-V" lines for explaining the specifications of the respective spring caps.

Fig. 6 is a perspective view showing the spring cover exploded from the spring support of the present embodiment.

Fig. 7 is a perspective view of the spring cover of fig. 6 assembled to the spring support and shown.

Fig. 8 is a sectional view showing a state in which the spring cover of fig. 7 is assembled to a spring supporter.

Fig. 9 is a sectional view showing a process of attenuating noise using a spring cover in the linear compressor of the present embodiment.

Fig. 10 is a graph for explaining the sound-deadening effect by the spring cover of the present embodiment.

Fig. 11 is a sectional view showing another embodiment of the spring cover.

Fig. 12A to 12C are sectional views showing still another embodiment of the spring cover.

Fig. 13A is a plan view showing the spring support member mounted with spring caps of different specifications, and fig. 13B to 13D are cross-sectional views of lines vi-vi, vi '-vi', vi "-vi" of the respective spring caps.

Fig. 14 is a sectional view showing still another embodiment of the spring cover.

Fig. 15 is a sectional view showing another embodiment of the arrangement position of the spring cover.

Fig. 16 is a sectional view showing still another embodiment of the arrangement position of the spring cover.

Detailed Description

Hereinafter, the linear compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

The linear compressor of the present embodiment is a device that performs operations for sucking and compressing a fluid and discharging the compressed fluid, and may be a component of a refrigeration cycle device. Hereinafter, an example in which a refrigerant circulating a refrigeration cycle is used as a fluid will be described. In the present embodiment, the reciprocating direction of the piston is defined as the axial direction, and the axis of the housing is defined to coincide with the respective axes of the frame, the cylinder, the piston, and the like. The following description will be made with the compression direction of the piston defined as the front side and the suction direction defined as the rear side.

Fig. 1 is a perspective view of an external appearance of the linear compressor of the present embodiment as viewed from a suction side, and fig. 2 is a cross-sectional view taken along line iv-iv of fig. 1, which is a cross-sectional view illustrating an interior of the linear compressor of the present embodiment.

Referring to fig. 1 and 2, the linear compressor of the present embodiment includes a compressor body C disposed inside a casing 110, and a piston 142 coupled to a mover 133 of the linear motor sucks and compresses a refrigerant while reciprocating inside a cylinder 141, and discharges the refrigerant.

The housing 110 may include: a cylindrical case 111 in a cylindrical shape; and a pair of casing covers 112, 113 coupled to both end portions of the cylindrical casing 111. The pair of housing covers 112, 113 may include: a first shell cover 112 on a refrigerant suction side as a rear side; and a second casing cover 113 positioned on the refrigerant discharge side, which is the front side.

The cylindrical housing 111 may be formed in a cylindrical shape extending long in the lateral direction. However, according to circumstances, the cylindrical housing 111 may also be formed in a cylindrical shape extending long in the longitudinal direction. In the present embodiment, an example in which the cylindrical casing 111 extends long in the lateral direction will be described as a center. Therefore, the longitudinal central axis of the cylindrical housing 111 coincides with the central axis of a compressor body C described later, and the central axis of the compressor body C coincides with the central axes of the cylinder tube 141 and the piston 142 constituting the compressor body C.

The inner diameter of the cylinder housing 111 may be formed in various sizes according to the size of the linear motor 130. The linear compressor of the present embodiment excludes the oil bearing and applies the gas bearing, thereby eliminating the need for filling oil in the inner space 110a of the casing 110. Therefore, the inner diameter of the cylindrical housing 111 may be preferably as small as possible, and may have a size of only an interval to the extent that the frame head 121 of the frame 120 described later does not contact the inner circumferential surface of the housing 110, for example. Thereby, the outer diameter of the cylindrical shell 111 of the linear compressor of the present embodiment can be formed to be small.

Both ends of the cylindrical casing 111 are open, and the first casing cover 112 and the second casing cover 113 may be coupled to the open both ends of the cylindrical casing 111, respectively. The first casing cover 112 may be coupled with the cylindrical casing 111 to seal a rear side, i.e., a right side open end, of the cylindrical casing 111, and the second casing cover 113 may be coupled with the cylindrical casing 111 to seal a front side, i.e., a left side open end, of the cylindrical casing 111.

Thereby, the inner space 110a of the housing 110 is sealed. A refrigerant suction pipe 1141 for guiding the refrigerant to the internal space 110a of the casing 110 may be penetratingly coupled to the first casing cover 112, and a refrigerant discharge pipe 1142 for guiding the compressed refrigerant to the refrigeration cycle and a refrigerant injection pipe 1143 for replenishing the refrigerant may be penetratingly coupled to the cylindrical casing 111, respectively.

A terminal bracket 115 is provided on the rear side surface of the cylindrical housing 111, and a terminal 1151 for transmitting an external power to the linear motor may be provided on the terminal bracket 115 so as to penetrate the cylindrical housing 111.

Next, the inside of the housing is explained.

Referring to fig. 2, a compressor body C is provided inside the cylindrical housing 111, and a rear side support spring (hereinafter, referred to as a first support spring) 1161 and a front side support spring (hereinafter, referred to as a second support spring) 1162 for supporting the compressor body C may be provided on the rear side and the front side of the compressor body C, respectively.

The first support spring 1161 may be formed as a plate spring provided between a rear surface of a rear cover 1612 to be described later and the first housing cover 112 facing the rear cover 1612, and the second support spring 1162 may be formed as a compression coil spring provided between an outer circumferential surface of a housing case 1555 to be described later and an inner circumferential surface of the cylindrical housing 111 facing the housing case 1555.

In addition, stoppers (stoppers) 1171, 1172 for restraining the compressor body C with respect to the casing 110 may be provided inside the casing 110. The stops 1171, 1172 may include: a first stopper 1171 for restraining the rear side of the compressor body C; and a second stopper 1172 for restraining the front side of the compressor body C.

The first stopper 1171 may be formed as a bracket provided to an inner circumferential surface of the cylindrical housing 111 to correspond to a rear cover 1612 described later, and the second stopper 1172 may be formed as a ring (ring) provided to an outer circumferential surface of a cover housing 1555 described later to correspond to an inner side surface of the second housing cover 113.

The first stopper 1171 may restrain the compressor body C in an axial direction (front-rear direction, lateral direction), and the second stopper 1172 may restrain the compressor body C in a radial direction. Thereby, it is possible to prevent the compressor body C from being damaged due to collision between the compressor body and the shell 110 caused by shaking, vibration, impact, or the like generated during transportation of the compressor.

Next, the compressor body C is explained.

Referring to fig. 2, the compressor body C of the present embodiment may include a frame 120, a motor unit 130 formed of a linear motor, a compression unit 140, a suction and discharge unit 150, and a resonance unit 160. The front sides of the motor unit 130 and the compression unit 140 are fixed to the frame 120, and the motor unit 130 and the compression unit 140 may be elastically supported by the resonance unit 160.

The frame 120 may include a frame head portion 121 and a frame body portion 122. The frame head portion 121 is formed in a disc shape, and the frame body portion 122 is formed to extend in a cylindrical shape from a rear side surface of the frame head portion 121.

The outer stator 131 described later may be coupled to the rear surface of the frame head 121, and the discharge cap assembly 155 described later may be coupled to the front surface of the frame head 121. An inner stator 132 described later may be coupled to an outer circumferential surface of the frame body 122, and a cylinder 141 may be coupled to an inner circumferential surface of the frame body 122.

The frame 120 includes a bearing inlet groove 125a, a bearing communication hole 125b, and a bearing communication groove 125c, which form a gas bearing passage portion (not denoted with a reference numeral).

A bearing inlet groove 125a is formed on the front surface side of the frame head portion 121, a bearing communication hole 125b is formed to penetrate from the rear surface of the bearing inlet groove 125a toward the inner circumferential surface of the frame body portion 122, and a bearing communication groove 125c may be formed on the inner circumferential surface of the frame body portion 122 to communicate with the bearing communication hole 125 b.

For example, the bearing inlet groove 125a may be formed to be recessed from the front surface of the frame head part 121 by a predetermined depth in the axial direction, and the bearing communication hole 125b may be formed as a hole having a smaller sectional area than that of the bearing inlet groove 125a, and may be formed to be inclined toward the inner circumferential surface of the frame body part 122.

The bearing communicating groove 125c may be formed in an annular shape having a predetermined depth and an axial length on the inner peripheral surface of the frame body 122. However, the bearing communicating groove 125c may be formed on the outer peripheral surface of the cylinder 141 in contact with the inner peripheral surface of the frame body 122, or may be formed in half on each of the inner peripheral surface of the frame body 122 and the outer peripheral surface of the cylinder 141.

Further, a gas bearing 1411 communicating with the bearing communicating groove 125c may be formed in the cylinder tube 141 corresponding to the bearing communicating groove 125 c. For the gas bearing, it will be explained later together with the cylinder tube.

Next, the motor unit 130 is explained.

Referring to fig. 2, the motor unit 130 of the present embodiment includes: a stator 130 a; and a movable mover (mover)130b reciprocating with respect to the stator 130 a.

The stator 130a may include an outer stator 131 and an inner stator 132. The outer stator 131 is fixed to the frame head 121 so as to surround the frame body 122 of the frame 120, and the inner stator 132 may be disposed inside the outer stator 131 with a predetermined gap 130c therebetween.

The outer stator 131 may include a coil winding body 1311 and an outer stator core 1312. The coil winding body 1311 may be accommodated inside the outer stator core 1312. However, the coil winding body 1311 may also be accommodated inside the inner stator 132, depending on the circumstances.

The coil winding body 1311 may include: a spool (bobbin)1311a formed in a ring shape; and a coil 1311b wound in the circumferential direction of the bobbin 1311 a. The bobbin 1311a may be provided with a terminal portion (not shown) that leads or exposes the power supply line led out from the coil 1311b to the outside of the outer stator 131.

The outer stator core 1312 may include a plurality of core blocks (core blocks) stacked in a circumferential direction of the bobbin 1311a so as to surround the coil winding body 1311. Each of the core blocks may be laminated by a plurality of lamination sheets (not denoted by reference numerals) formed in a shape of "Contraband".

A stator cover 1611 for fixing the outer stator 131 may be provided at the rear side of the outer stator 131. For example, the front surface of the outer stator 131 is supported by the frame head 121, and the rear surface thereof is supported by the stator cover 1611. Further, the cover fastening member 136 formed in a rod shape penetrates the stator cover 1611, and may be inserted and fixed to the frame head 121 through the edge of the outer stator 131. Thereby, the motor unit 140 can be stably fixed between the rear surface of the frame head 121 and the front surface of the stator housing 1611 by the housing fastening member 136.

Here, the stator cover 1611 supports not only the outer stator 131 but also a front side spring described later. Therefore, the stator housing 1611 forms not only a part of the motor unit 130 but also a part of the resonance unit 160. In the present embodiment, the stator housing 1611 is classified as a part of the resonance unit 160, which will be described again later together with the resonance unit.

The inner stator 132 may be inserted into and coupled to the outer circumferential surface of the frame body 122. A plurality of lamination sheets (not denoted with reference numerals) of the inner stator 132 forming an inner stator core (not denoted with reference numerals) may be laminated in a circumferential direction outside the frame main body portion 122 so as to surround the frame main body portion 122.

The movable cell 130b includes: a magnet frame 1331; and a magnet 1332 supported by the magnet frame 1331.

The magnet frame 1331 may be formed in a cylindrical shape having a front surface opened and a rear surface sealed. Thus, the front side of the magnet frame 1331 is inserted from the rear side of the motor unit 130 toward the front side, so as to be positioned in the gap between the outer stator 131 and the inner stator 132, and the rear side of the magnet frame 1331 is positioned between the rear side of the motor unit 130 and the front side of the resonance unit 160.

The magnet 1332 may be fixedly provided on the outer circumferential surface of the front side of the magnet frame 1331. For example, a magnet insertion groove (not shown) may be formed on the outer circumferential surface of the magnet frame 1331 on the front side, and the magnet 1332 may be inserted into and coupled to the magnet insertion groove. The magnet 1332 may be divided into a plurality and fixed at a predetermined interval in a circumferential direction, or may be formed in a cylindrical shape and fixed.

A muffler insertion hole 1331a is formed at the center of the rear surface of the magnet frame 1331, and the suction muffler 151 may be penetratingly coupled to the muffler insertion hole 1331 a. As for the suction muffler 151, it will be described again later.

The spring supporter 1613 may be coupled to a rear side surface of the magnet frame 1331 together with the later-described piston 142. For the piston and the spring support, it will be explained again later together with the compression unit and the resonance unit.

Next, the compression unit 140 will be explained.

Referring to fig. 2, the compression unit 140 of the present embodiment may include a cylinder 141, a piston 142, a suction valve 143, a discharge valve assembly 144, a suction muffler 151, and a discharge cap assembly 155.

The cylinder 141 may be formed of a material that is light and excellent in workability, such as an aluminum material (aluminum or aluminum alloy). The cylinder 141 may be formed in a cylindrical shape and insert-fixed to the inside of the frame 120.

The piston 142 is inserted into the cylinder 141 and reciprocates, thereby forming a compression space V inside the front side of the cylinder 141. The compression space V is interposed between the suction valve 143 and the discharge valve assembly 144, which will be described later, and communicates with the suction flow path 1421 of the piston 142 and the discharge space S of the discharge valve assembly 144, which will be described later.

The cylinder 141 may be formed with a gas bearing 1411. The gas bearing 1411 is formed to penetrate between the outer circumferential surface and the inner circumferential surface of the cylinder tube 141 in the radial direction from a position communicating with the bearing communication groove 125 c. Thereby, a part of the refrigerant discharged into the discharge space S is supplied to the bearing surface between the inner peripheral surface of the cylinder tube 141 and the outer peripheral surface of the piston 142 via the gas bearing passage portion (no reference numeral) and the gas bearing 1411. The refrigerant can float the piston 142 from the cylinder 141 by forming a high pressure, and can reciprocate the piston 142 while being spaced apart from the cylinder 141.

Here, the range of the bearing surface may be changed according to the reciprocating motion of the piston 142. Therefore, the front side of the bearing surface may communicate with the compression space V, and the rear side thereof may communicate with the inner space 110a of the casing 110 forming the suction space.

At this time, if the gas bearing 1411 is formed excessively close to the compression space V or the suction space, the high-pressure refrigerant supplied to the bearing surface leaks to the compression space V or the suction space, so that the efficiency of the compressor may be reduced. Therefore, the gas bearing 1411 may preferably be formed at a position not directly communicating with the compression space V or the suction space.

Like the cylinder 141, the piston 142 may be formed of an aluminum material. The piston 142 may be formed in a cylindrical shape in which a front end is partially opened and a rear end thereof is completely opened.

In addition, a rear end as an open end of the piston 142 may be connected to the magnet frame 1331. Thereby, the piston 142 can reciprocate together with the magnet frame 1331.

Further, a suction flow path 1421 is formed to penetrate the interior of the piston 142 in the axial direction, and a suction port 1422 for communicating the suction flow path 1421 with the compression space V is formed at the front end of the piston 142. The suction port 1422 may be formed with only one suction port at the center, or may be formed with a plurality of suction ports at the edge.

A suction valve 143 for selectively opening and closing the suction port 1422 may be provided on the front surface of the piston 142.

The suction valve 143 is formed of a thin steel plate, and may be fastened to a front end surface of the piston 142 by bolts. The suction valve 143 may be formed of a guide valve having one or more opening and closing portions.

The discharge valve assembly 144 may be provided at the front end of the cylinder 141 so as to be able to open and close the discharge side of the compression space V. The discharge valve assembly 144 can be accommodated in a discharge space S of a discharge cap assembly 155 described later.

The discharge valve assembly 144 may include a discharge valve 1441, a valve spring 1442, and a spring support member 1443.

The discharge valve 1441 may be constituted by a valve body 1441a facing the cylinder tube 141 and a spring coupling portion 1441b facing the discharge cap assembly 155. The valve body portion 1441a and the spring coupling portion 1441b may be integrally formed, or may be separately manufactured and then assembled.

In addition, the valve body portion 1441a is formed in a circular disk shape or a hemispherical shape, and the spring coupling portion 1441b extends in a rod shape, and may be formed in an axial direction from the center of the front surface of the valve body portion 1441 a.

In addition, the valve body portion 1441a may be formed by including carbon fibers in a resin. The carbon fibers may be irregularly arranged, or may be formed in a regular arrangement form such as a lattice shape or one-directional arrangement. For example, in the case where the carbon fibers are regularly arranged, it is preferable to arrange the carbon fibers in parallel with the front end surface of the cylinder tube 141 so that damage to the cylinder tube can be reduced at the time of collision.

The valve spring 1442 may be formed as a plate spring or a compression coil spring. The valve spring 1442 of the present embodiment is formed as a plate spring in a circular disk shape, and may be coupled with the spring coupling portion 1441 b.

The spring support member 1443 is formed in a ring shape, and an edge of the valve spring 1442 may be surrounded by an inner circumferential surface of the spring support member 1443 and insert-coupled to the spring support member 1443. The thickness of the spring support member 1443 is formed to be thicker than the thickness of the valve spring 1442, thereby generating an elastic force to the valve spring 1442.

Next, the suction/discharge unit 150 will be described.

Referring to fig. 2, the suction and discharge unit 150 of the present embodiment includes a suction muffler 151 and a discharge cap assembly 155. The compression space V is interposed between the suction muffler 151 and the discharge cap assembly 155, the suction muffler 151 is disposed on the suction side, and the discharge cap assembly 155 is disposed on the discharge side.

The suction muffler 151 may be inserted into the suction flow path 1421 of the piston 142 through the muffler insertion hole 1331a of the magnet frame 1331. Thus, the refrigerant sucked into the internal space 110a of the casing 110 flows into the suction flow path 1421 through the suction muffler 151, opens the suction valve 143, and is sucked into the compression space V in the cylinder tube 141 through the suction port 1422 of the piston 142.

In addition, the suction muffler 151 may be fixed to a rear surface of the magnet frame 1331. For example, the suction muffler 151 is coupled to the piston 142 described later. The suction muffler 151 may reduce flow noise of the refrigerant generated in a process in which the refrigerant is sucked into the compression space V through the suction flow path 1421 of the piston 142.

In addition, the suction muffler 151 may include a plurality of mufflers. For example, the plurality of mufflers may include a first muffler 1511, a second muffler 1512, and a third muffler 1513 that are combined with one another.

The first muffler 1511 is located inside the piston 142, and the second muffler 1512 is coupled to a rear end of the first muffler 1511. Further, the third muffler 1513 accommodates the second muffler 1512 inside thereof, and the front end portion may be coupled to the rear end of the first muffler 1511. Thus, the refrigerant may sequentially pass through the first muffler 1511, the second muffler 1512, and the third muffler 1513. In this process, the flow noise of the refrigerant can be attenuated.

In addition, a muffler filter 1514 may be mounted on the suction muffler 151. The muffler filter 1514 may be located at the interface where the second muffler 1512 and the third muffler 1513 are joined. For example, the muffling filter 1514 may have a circular shape, and the edge of the muffling filter 1514 may be supported while being placed between the joining faces of the second muffler 1512 and the third muffler 1513.

The discharge cap assembly 155 accommodates the discharge valve assembly 144, and may be coupled to a front surface of the frame 120. The discharge cap assembly 155 may be formed of one discharge cap, or may be formed of a plurality of discharge caps. For convenience of explanation, the discharge cap assembly 155 of the present embodiment is configured such that a plurality of discharge caps are overlapped, and for convenience of explanation, the discharge cap located on the inner side is divided into discharge caps in the discharge order of the refrigerant, and the discharge cap located on the outer side is divided into a cap housing.

For example, the spit cap assembly 155 may include: a spit-out cap 1551 for accommodating the spit-out valve assembly 144; and a cap housing 1555 for accommodating the spit-out cap 1551 and fixed to a front surface of the frame 120. The spit-out cap 1551 is formed of a high temperature resistant engineering plastic, and the cap housing 1555 may be formed of an aluminum die cast.

The spit-out cap 1551 may include: a housing body portion 1551 a; a cover flange section 1551b extending in the radial direction from the outer peripheral surface of the cover body section 1551 a; and a cover protrusion 1551c extending forward from the cover flange portion 1551 b.

The cover body 1551a is formed in a container shape having an open rear surface and a closed front surface, and can be inserted into an outer discharge space S2 of a cover housing 1555 described later. The inner space of the cap main body 1551a forms an inner discharge space S1. Since the discharge valve assembly 144 is accommodated in the inner discharge space S1, the inner discharge space S1 forms a first discharge space when viewed in the order of refrigerant discharge.

There may be formed: a cover boss part 1551d extending from the center of the front surface of the cover body part 1551a in the direction of the discharge valve assembly 144. The cover boss portion 1551d may be formed in a cylindrical shape, and a communication hole 1551e for communicating the inner discharge space S1 of the discharge cover 1551 with the outer discharge space S2 of the cover housing 1555 may be formed at the center of the rear surface of the cover boss portion 1551 d. Therefore, the second discharge space is formed in the outer discharge space S2 when viewed in the order of refrigerant discharge.

The housing flange 1551b may be formed to extend in a flange shape from the outer peripheral surface of the housing main body 1551a on the front side. A rear surface of the cap flange 1551b is in close contact with a spring support member 1443 forming a part of the discharge valve assembly 144 and can be axially supported, and a front surface of the cap flange 1551b is in close contact with a cap support part 1555b of a cap housing 1555 described later and can be axially supported.

A cover protrusion 1551c may be formed extending from an edge of the front surface of cover flange portion 1551b toward the inner side of cover housing 1555. The cover protrusion 1551c may be formed in a cylindrical shape. Thus, the outer peripheral surface of the cover protrusion 1551c is closely attached to the inner surface of a housing peripheral wall 1555a of the cover housing 1555 described later, and can be supported in the radial direction.

On the other hand, the cover case 1555 is fixed to the front surface of the frame head 121, and an outer discharge space S2 is formed inside the cover case 1555. One side of the outer discharge space S2 is communicated with the inner discharge space S1 of the discharge cover 1551 via the communication hole 1551e of the discharge cover 1551, and the other side of the outer discharge space S2 can be connected to the refrigerant discharge pipe 1143 via the annular pipe 1444.

For example, the cover housing 1555 is formed in a container shape in which the front surface is closed and the rear surface is opened. A housing peripheral wall 1555a for forming a side wall surface of the cover housing 1555 is formed in a substantially cylindrical shape, and a rear end of the housing peripheral wall 1555a can be closely bonded to a front surface of the frame 120 via a heat insulating member (no reference numeral).

Inside the cover housing 1555, a cover support part 1555b extending from the inner front surface toward the frame 120 may be extended. The cover support portion 1555b may be formed in a cylindrical shape with a predetermined interval from the housing peripheral wall portion 1555a of the cover housing 1555. Thus, the inner space of the cover housing 1555 can be divided into an inner space and an outer space in the radial direction by the cover support part 1555 b.

The cap body 1551a of the discharge cap 1551 is inserted into the space inside the cap housing 1555, the cap projection 1551c of the discharge cap 1551 is inserted into the space outside the cap housing 1555, and the cap flange 1551b of the discharge cap 1551 is axially supported by the front end of the cap support 1555 b.

A pipe (pipe) coupling portion (not shown) is formed on the peripheral wall surface of the cover case 1555, and one end of the annular pipe 1444 bent multiple times in the internal space 110a of the housing 110 is connected to the pipe coupling portion. The other end of the annular pipe 1444 is connected to the refrigerant discharge pipe 1143. Thus, the refrigerant discharged into the outer discharge space S2 is guided to the refrigerant discharge pipe 1143 through the annular pipe 1444, and the refrigerant can be guided to the refrigeration cycle apparatus through the refrigerant pipe.

Next, the resonance unit 160 is explained.

Referring to fig. 2, the resonance unit 160 of the present embodiment may include a support 161 and a spring 162 supported by the support.

The support portion 161 may be formed of members that support the front and rear ends of the spring 162, respectively. For example, the support portion 161 may be formed of a stator case 1611, a rear case 1612, and a spring supporter 1613.

As described above, stator housing 1611 is closely attached to the rear surface of outer stator 131, and is fastened to frame 120 by housing fastening member 136, and rear housing 1612 is fastened and fixed to the rear surface of stator housing 1611. Further, a spring support 1613 is coupled to the magnet frame 1331 and the piston 142, and is located between the stator housing 1611 and the rear housing 1612.

Thus, the stator housing 1611 can be disposed on the front side and the rear housing 1612 can be disposed on the rear side with respect to the spring stay 1613. Further, a first spring 1621, which will be described later, may be disposed between the stator housing 1611 and the spring support 1613, and a second spring 1622, which will be described later, may be disposed between the spring support 1613 and the rear housing 1612.

As described above, the stator housing 1611 is formed in a ring shape, the rear housing 1612 is formed with the support leg portions 1612a and is spaced from the stator housing 1611 in the axial direction, and a support body portion 1616 described later may extend in the axial direction, so that the spring support 1613 may be spaced from the stator housing 1611 and the rear housing 1612, respectively, in the axial direction.

The support member main body portion 1616 may be formed to be smaller than the support leg portion 1612a of the rear cover 1612 by about half the length thereof. Thus, a spring support portion 1617 of a spring support 1613 described later can be disposed at an intermediate position between the stator housing 1611 and the rear housing 1612.

However, the spring 162 may be formed of one spring, and in this case, the spring supporter 1613 may be omitted. However, in the present embodiment, description will be made mainly on an example of the spring 162 in which the first spring 1621 is provided on the front side and the second spring 1622 is provided on the rear side via the spring support 1613.

The spring support 1613 is fixedly secured to the rear surface of the magnet frame 1331. Thereby, the spring supporter 1613 is integrally combined with the magnet frame 1331 and the piston 142 to reciprocate along a straight line together.

For example, the spring supporter 1613 may include a supporter fixing portion 1615, a supporter main body portion 1616, and a spring supporting portion 1617.

The support fixing portion 1615 is formed in a disk shape, and a muffler insertion hole 1615a for penetrating the suction muffler 161 may be formed at a central portion thereof. And the fastening hole 1615b and the refrigerant through hole 1615c may be formed along the circumference of the muffler insertion hole 1615 a.

The supporter main body portion 1616 has a cylindrical shape bent from an edge of the support fixing portion 1615 toward a rear side, and may have a plurality of refrigerant through holes 1615c formed along a circumferential direction. However, the support main body portion 1616 is not necessarily limited to a cylindrical shape. For example, the support member main body portion 1616 may be formed in a plurality of leg shapes arranged at a predetermined interval in the circumferential direction.

The spring support portion 1617 may extend in a radial direction from an end of the support main body portion 1616 toward the outside. The plurality of spring support portions 1617 may be provided, and the plurality of spring support portions 1617 may be formed at a predetermined interval in the circumferential direction.

However, the spring supporting portion 1617 may be formed in a flange shape. However, when the spring support portion 1617 is formed in the shape of one flange, the inner diameter of the rear cover 1612 needs to be increased in consideration of interference with the rear cover 1612, which will be described later, and therefore the size of the compressor may be increased accordingly.

Therefore, the plurality of spring support portions 1617 of the present embodiment are spaced apart by a predetermined interval in the circumferential direction, and the support leg portions 1612a of the rear cover 1612 may be coupled in such a manner as to be alternately disposed between the spring support portions 1617 in the circumferential direction. Accordingly, since it is not necessary to increase the inner diameter of the rear cover 1612, the size of the compressor can be suppressed from increasing accordingly.

Referring to fig. 2, the spring cover 163 is coupled to the plurality of spring support portions 1617, respectively, and an end portion of the spring 162 may be inserted and fixed to the spring cover 163. Thereby, the spring 162 can be kept assembled to the spring support portion 1617.

To this end, cover support holes 1617a are formed in the plurality of spring support portions 1617, respectively. The cover support hole 1617a may be formed according to the number and position of the first and second springs 1621 and 1622 opposite to each other.

For example, as shown in the present embodiment, in the case where the first spring 1621 is coupled to the front side of the spring support portion 1617 and the second spring 1622 is coupled to the rear side of the spring support portion 1617, two cover support holes 1617a may be formed at each spring support portion 1617. Further, the spring cover 163 may be respectively inserted and fixed to each cover support hole 1617 a.

Thus, the first spring 1621 and the second spring 1622 have six, respectively, and in the case where the six first springs 1621 and the six second springs 1622 are divided into two springs, respectively, to be supported by the three spring support portions 1617, a total of 12 spring covers 163 may be provided on the front surface and the rear surface of the spring support portion 1617, respectively. Hereinafter, a spring cover disposed on a front surface of the spring support portion 1617 and coupled to the first spring 1621 will be defined as a first cover 1631, and a spring cover disposed on a rear surface of the spring support portion 1617 and coupled to the second spring 1622 will be defined as a second cover 1632.

The plurality of spring caps 163 may be formed identically. For example, each of the spring covers 163 disposed in the circumferential direction may be formed of a first cover 1631 and a second cover 1632 having the same shape.

Here, the first cover 1631 and the second cover 1632 may be formed to be symmetrical with respect to the respective spring support portions 1617, or may be formed to be different. That is, the shape thereof may be variously formed as long as the spring cover 163 can function as a noise reduction device such as a Helmholtz Resonator (Helmholtz Resonator).

In this embodiment, first, an example of the first cover 1631 and the second cover 1632 formed to be slightly different from each other will be mainly described. Further, as for an example in which the first cover 1631 and the second cover 1632 are symmetrically formed, it will be described later in another embodiment.

Referring to fig. 2, the spring 162 may include a first spring 1621 and a second spring 1622.

The first and second springs 1621 and 1622 may be formed as compression coil springs. The first spring 1621 and the second spring 1622 may be arranged to correspond to each other in the axial direction with the spring support portion 1617 interposed therebetween.

For example, a front end of each first spring 1621 may be supported on a rear surface of the stator housing 1611, and a rear end of each first spring 1621 may be supported on a front surface of the spring support 1617. A spring support protrusion 1611a is formed at a rear surface of the stator housing 1611 such that a front end of the first spring 1621 is inserted and supported, and the aforementioned first cover 1631 may be coupled at a front surface of the spring support portion 1617.

In addition, a front end of each second spring 1622 may be supported at a rear surface of the spring support 1617, and a rear end of each second spring 1622 may be supported at a front surface of the rear cover 1612. The aforementioned second cover 1632 is combined to a rear surface of the spring support portion 1617, and a second spring support boss 1612b may be formed on a front surface of the rear cover 1612 such that a rear end of the second spring 1622 is inserted and supported.

Thus, each of the first springs 1621 is disposed at the front side of the spring support 1613, and each of the second springs 1622 is disposed at the rear side of the spring support 1613, so that the first and second springs 1621 and 1622 can resonate the mover 133 and the piston 142 while extending and contracting opposite to each other.

The linear compressor of the present embodiment described above operates as follows.

That is, when current is applied to the winding coil 134 of the motor unit 130, magnetic flux is formed between the outer stator 131 and the inner stator 132, and the magnet frame 1331 and the mover 130b formed of the magnet 133b reciprocate through a gap between the outer stator 131 and the inner stator 132 by electromagnetic force generated by the magnetic flux.

Then, the volume of the compression space V will increase or decrease while the piston 142 connected to the magnet frame 130b is reciprocated in the cylinder 141 along the axial direction. At this time, when the piston 142 moves backward to increase the volume of the compression space V, the suction valve 143 is opened, and the refrigerant in the suction flow path 1421 is sucked into the compression space V, and when the piston 142 moves forward to decrease the volume of the compression space V, the pressure of the compression space V increases. Then, the refrigerant compressed in the compression space V is discharged to the first discharge space S1 of the discharge cover 1551 while opening the discharge valve 1441.

Then, the refrigerant discharged into the first discharge space S1 moves to the second discharge space S2 of the cover housing 1555 through the communication hole 1551 e. At this time, a part of the refrigerant moving from the first discharge space S1 toward the second discharge space S2 flows into the bearing inlet groove 125a forming an inlet of the gas bearing, the refrigerant is supplied to the bearing surface between the inner peripheral surface of the cylinder tube 141 and the outer peripheral surface of the piston 142 via the bearing communication hole 125b, the bearing communication groove 125c, and the gas bearing 1411 of the cylinder tube 141, the high-pressure refrigerant supplied to the bearing surface lubricates between the cylinder tube 141 and the piston 142, a part of the refrigerant flows out to the compression space V, and the remaining refrigerant flows out to the suction space, i.e., the internal space 110a of the housing 110.

The refrigerant that has flowed into the second discharge space S2 is discharged to the outside of the compressor via the annular pipe 1444 and the refrigerant discharge pipe 1142, and thus a series of processes of moving toward the condenser of the refrigeration cycle are repeated in this manner.

On the other hand, during the operation of the compressor, noises of various frequency bands are generated and transmitted to the outside of the casing. Therefore, the noise of the compressor has been attenuated by providing an additional sound attenuation means such as a dynamic vibration absorber inside or outside the casing.

However, in the case where the muffler device is provided inside the casing, not only the manufacturing cost is increased due to the increase in the number of parts and the number of assembly processes, but also the compressor may be enlarged due to the increase in the volume of the casing. In addition, in the case where the muffler is provided outside the casing, not only the manufacturing cost described above is increased or the compressor is enlarged, but also the appearance of the compressor may be complicated.

Therefore, the present embodiment aims to effectively cancel the noise of the compressor using the existing parts without providing an additional muffler inside or outside the casing.

Fig. 3 is a perspective view of the compressor body of fig. 1 as viewed from the rear side, and fig. 4 is a perspective view illustrating the resonance unit of fig. 3 in an exploded view.

Referring to fig. 3 and 4, the spring supporter 1613 of the present embodiment is formed with a plurality of spring supporting portions 1617. Each spring support portion 1617 extends from a rear end of the support main body portion 1616, and is bent in a radial direction.

The plurality of spring support portions 1617 are formed at predetermined intervals along the circumferential direction. For example, a plurality of spring supporting parts 1617 are arranged at equal intervals of 120 degrees, and each spring supporting part 1617 may be formed identically.

Each of the spring support portions 1617 is formed in a long circular arc shape along the circumferential direction, and two cover support holes 1617a may be formed at each of the spring support portions 1617 at a predetermined interval along the circumferential direction.

The cover support holes 1617a may all be formed the same. For example, the cover support holes 1617a may be formed to have the same inner diameter and to penetrate the spring support portion 1617 in the axial direction.

In addition, the spring cover 163 may be inserted into and coupled to the cover support hole 1617 a. The spring cover 163 is formed of a first cover 1631 and a second cover 1632, and thus can be inserted from both sides in the axial direction of the cover support hole 1617a, respectively. The spring cover 163 may be formed to have the same specification in the circumferential direction, or may be formed to have a different specification.

Here, the specification may be defined as the same meaning as the shape. That is, the spring cover 163 is a helmholtz resonator, and thus, it is understood that the same specification means that the same shape is formed, and the noise of the same frequency band Hz can be attenuated. Therefore, hereinafter, the expression that the spring caps 163 have the same or symmetrical shape is understood to mean that the specifications of the spring caps 163 are the same.

Fig. 5A is a plan view showing a spring supporter to which spring caps of the same specification are mounted, and fig. 5B to 5D are sectional views of V-V, V '-V', V "-V" lines for explaining the specifications of the respective spring caps.

Referring to fig. 5A, the spring covers 163 of the present embodiment are coupled to each of the cover support holes 1617a provided at each of the spring support portions 1617, and each of the spring covers 163 may be formed to have the same shape.

For example, in the case where each of the spring supporting parts 1617 of the spring support 1613 is provided with two spring covers 163, respectively, the two spring covers 163 may be formed to have the same shape as the other two adjacent spring covers 163.

That is, when (V-V, V '-V', V "-V") is cut and each spring cover 163 mounted to each spring support portion 1617 is observed, the volume of the space portion 163a, the sectional area of the passage portion 163b, and the length of all the spring covers 163 may be formed to be the same. In fig. 5B to 5D, the case where the sectional areas of the passage portions all have the same sectional area a is symbolically shown.

Hereinafter, a description will be given of a typical example of one spring support portion 1617 and one cover support hole 1617 a. Fig. 6 is a perspective view showing the spring cover exploded from the spring support of the present embodiment. Fig. 7 is a perspective view of the spring cover of fig. 6 assembled to the spring support and shown. Fig. 8 is a sectional view showing a state in which the spring cover of fig. 7 is assembled to a spring supporter.

Referring to fig. 6 and 7, the spring cover 163 of the present embodiment includes: a space portion 163a formed inside the spring cover 163; and a passage part 163b penetrating the surface of the spring cover 163 to communicate with the space part 163 a.

The space part 163a has an arbitrary volume, and may be separated from the internal space 110a of the case 110. For example, a pair of covers 1631 and 1632 having an opening on one side in the axial direction are coupled to face each other from both sides in the axial direction, so that a space 163a can be formed inside the covers 1631 and 1632.

However, the space portion 163a does not necessarily need to be formed by combining two pairs of covers 1631, 1632. For example, space portion 163a may be formed inside one cover formed in a cylindrical shape by cutting both ends of the cover having a hollow shape.

The passage section 163b is a passage for communicating the inside of the space section 163a with the outside of the space section 163 a. Since the passage 163b of the present embodiment forms a neck portion (neck portion) of the helmholtz resonator, the frequency band to be attenuated can be adjusted according to the length of the passage 163 b.

The passage portion 163b may be formed in a cylindrical shape having a predetermined length. However, the passage portion 163b may be formed in a simple hole shape penetrating through a side surface of the cover for forming the space portion 163a, instead of extending from the side surface of the cover.

In addition, an inner diameter D2 of the passage part 163b is formed to be smaller than an inner diameter D1 of the space part 163a, and may be formed to penetrate a side surface of the spring cover 163 in the axial direction so that the space part 163a communicates with the inner space 110a of the housing 110. For example, the passage 163b may be formed to penetrate through the axial side surface of one of the two pair of caps 1631 and 1632, or may be formed to penetrate through the side surface of one hollow cap. The present embodiment describes the former, i.e., an example in which two paired covers 1631 and 1632 are coupled to form space portion 163a, as a typical example.

For example, the spring cover 163 of the present embodiment may include: a first cover 1631 coupled to a front surface of the spring support 1617; and a second cover 1632 coupled to a rear surface of the spring support portion 1617.

The first cover 1631 and the second cover 1632 are inserted into the front side and the rear side of the cover support hole 1617a provided in the spring support portion 1617, respectively. Thus, the first cover 1631 and the second cover 1632 can communicate with each other via the cover support hole 1617a, so that the aforementioned space portion 163a can be formed inside the spring cover 163.

The first cover 1631 of the present embodiment may include a first hole insertion part 1631a, a first cover support part 1631b, and a first spring insertion part 1631 c. The first hole insertion part 1631a and the first spring insertion part 1631c form an inner space of the first cover 1631, and form a first space part 163a1 substantially constituting a part of the space part 163.

The first hole insertion portion 1631a may be inserted in front of (hereinafter, referred to as a first side surface) the cover support hole 1617 a. The first hole insertion part 1631a may be formed to be smaller than the axial length t1 of the cover support hole 1617 a. For example, the axial length t21 of the first hole insertion part 1631a may be formed to be about 1/2 or less of the axial length t1 of the cover support hole 1617 a. The axial length t22 of the second hole insertion part 1632a described later may be formed to be about 1/2 or less of the axial length t1 of the cover support hole 1617 a. Thus, it can be inserted and coupled to the first and second hole insertion parts 1631a and 1632a, respectively, from both sides of the cover supporting hole 1617 a.

The first hole insertion portion 1631a may be formed in a cylindrical shape with both ends open. Thus, the first hole insertion portion 1631a communicates with the cover support hole 1617a and a second hole insertion portion 1632a described later, thereby forming a part of the space portion 163 a.

The first cover support part 1631b may be formed to extend in a flange shape from an outer circumferential surface of the first hole insertion part 1631 a. The outer diameter of the first cover supporting part 1631b may be formed to be larger than the inner diameter of the cover supporting hole 1617 a. Thereby, the first cover support 1631b is supported at the front surface of the spring support 1617 in the axial direction, and the end of the first spring 1621 may be supported at the front surface of the first cover support 1631b in the axial direction.

The first spring insertion part 1631c may be formed to extend from the first cover support part 1631b toward the opposite side of the first hole insertion part 1631 a. The inner diameter of the first spring insertion portion 1631c may be formed to have the same inner diameter in the axial direction. This can increase the volume of first space portion 163a 1.

In addition, the outer diameter of the first spring insertion part 1631c is formed to be smaller than the inner diameter of the first spring 1621, and may be formed to become smaller as being distant from the spring support 1617. This can suppress interference with the first spring 1621 inserted into the first spring insertion portion 1631 c.

The first spring insertion portion 1631c may be formed in a shape in which the rear side surface thereof is completely opened to communicate with the first hole insertion portion 1631a, and a part of the front side surface thereof is opened. Thus, the first spring insertion portion 1631c is formed in a container shape having a hollow space therein, thereby forming another part of the space portion 163a together with the interior of the second spring insertion portion 1632c described later.

However, most of the front side surface of the first spring insertion portion 1631c is blocked, and the channel portion 163b opened in the center thereof is formed. For example, a refrigerant inlet and outlet hole 1631d may be formed in a front side surface of the first spring insertion portion 1631c, and a refrigerant guide protrusion 1631e may be formed to extend in the axial direction from the periphery of the refrigerant inlet and outlet hole 1631 d.

The refrigerant inlet and outlet hole 1631d and the refrigerant guiding protrusion 1631e form the aforementioned channel portion 163 b. The sectional area a of the refrigerant inlet/outlet hole 1631d and the axial length L1 of the refrigerant guiding protrusion 1631e can be adjusted according to the specific frequency band to be cancelled.

The first spring insertion portion 1631c is formed in a container shape having a hollow space formed therein, and thus forms another part of the space portion 163a together with the interior of the second spring insertion portion 1632c described later. Only, a portion of the axial side surface of the front side of the first spring insertion portion 1631c may be opened to form the aforementioned passage portion 163 b. The passage portion 163b may be formed in a cylindrical shape having a predetermined length in the axial direction.

On the other hand, the second cover 1632 of the present embodiment may include a second hole insertion part 1632a, a second cover support part 1632b, and a second spring insertion part 1632 c. The second hole insertion portion 1632a and the second spring insertion portion 1632c form an inner space of the second cover 1632, and form a second space portion 163a2 substantially constituting a part of the space portion 163.

The second hole insertion part 1632a may be inserted from the rear (hereinafter, referred to as a second side) of the cover support hole 1617 a. The axial length t22 of the second hole insertion part 1632a may be formed to be smaller than the axial length t1 of the cover support hole 1617 a. For example, the axial length t22 of the second hole insertion part 1632a may be formed to be about 1/2 or less of the axial length t1 of the cover support hole 1617 a.

In addition, the second hole insertion portion 1632a may be formed in a cylindrical shape with both ends thereof opened. Thus, the second hole insertion portion 1632a communicates with the cover support hole 1617a and the first hole insertion portion 1631a, thereby forming a part of the space portion 163 a.

The second cover support part 1632b may be formed to extend in a flange shape from an outer circumferential surface of the second hole insertion part 1632 a. The outer diameter of the second cover supporting part 1632b may be formed to be larger than the inner diameter of the cover supporting hole 1617 a. Thereby, the second cover supporting part 1632b is supported at the rear surface of the spring supporting part 1617 in the axial direction, and the end of the second spring 1622 may be supported at the rear surface of the second cover supporting part 1632b in the axial direction.

The second spring insertion part 1632c may be formed to extend from the second cover support part 1632b toward the opposite side of the second hole insertion part 1632 a. The inner diameter of the second spring insertion portion 1632c may be formed to have the same inner diameter in the axial direction. This can increase the volume of the second space portion 163a 2.

In addition, the outer diameter of the second spring insertion part 1632c is formed to be smaller than the inner diameter of the second spring 1622, and may be formed to become smaller as being distant from the spring support 1617. This can suppress interference with the second spring 1622 inserted into the second spring insertion portion 1632 c.

The second spring insertion portion 1632c may be formed in a shape in which the front axial side surface thereof is opened so as to communicate with the second hole insertion portion 1632a, and the rear axial side surface thereof is closed. Thus, the second spring insertion portion 1632c is formed in a container shape having a hollow space therein, thereby forming another part of the space portion 163a together with the inside of the first spring insertion portion 1631 c.

The spring cover of the present embodiment as described above functions and effects as follows.

That is, when the piston 142 reciprocates in the axial direction together with the mover 133, the spring support 1613 coupled to the mover 133 and the piston 142 also reciprocates in the axial direction together. At this time, the first spring 1621 disposed at the front side of the spring supporter 1613 and the second spring 1622 disposed at the rear side of the spring supporter 1613 expand and contract in opposite directions to each other, and at the same time, the mover 133 and the piston 142 perform a resonant motion.

Here, spring covers 1631 and 1632 for supporting the rear end of the first spring 1621 and the front end of the second spring 1622 are provided on the spring support 1613 so as to reciprocate in the axial direction together with the spring support 1613.

The spring cover 163 of the present embodiment is formed with the space part 163a and the passage part 163b which function as a kind of resonator, whereby noise transmitted to the inner space 110a of the housing 110 is cancelled out in the process of the spring cover 163 reciprocating in the axial direction.

Fig. 9 is a sectional view showing a process of attenuating noise using a spring cover in the linear compressor of the present embodiment.

Referring to fig. 9, when the spring cap 163 reciprocates (or resonates) together with the mover 133 and the piston 142, the refrigerant filled in the internal space 110a of the housing 110 flows into the space portion 163a via the passage portion 163b, and then flows out from the space portion 163a to the internal space 110a of the housing 110 via the passage portion 163 b. In this process, noise generated in the compressor body C and the like is cancelled in the inner space 110a of the casing 110 by the helmholtz effect generated by the spring cover 163.

In general, a helmholtz resonator can cancel noise in a specific frequency band by the area and length of the passage portion 163b for forming a neck portion and the volume of the space portion 163a for forming a volume portion. Thus, if the internal volume of the spring cover 163 for forming the space portion 163a, and the area and length of the passage portion 163b are appropriately adjusted, noise in a specific frequency band (for example, 800Hz) can be cancelled.

Fig. 10 is a graph for explaining the sound-deadening effect by the spring cover of the present embodiment.

Referring to fig. 10, it can be seen that there is a significant noise attenuation effect in the 800Hz frequency band. Here, as described above, the suction noise and the discharge noise are attenuated only by the suction muffler 151 and the discharge cap assembly 155, but the noise in the frequency band (for example, 800Hz) that cannot be removed by these muffling devices still exists. However, as a result of properly adjusting and applying the space part 163a and the passage part 163b of the spring cover 163 of the present embodiment, it can be seen that noise in this frequency band can be attenuated as shown in the graph.

According to this manner, since noise is removed by the spring cover, noise generated in the inside of the housing can be effectively offset.

In addition, the noise generated in the inner part of the shell is offset without additionally arranging an additional silencer, so that the manufacturing cost of the compressor can be reduced, and the weight increase of the compressor can be restrained.

In addition, it is possible to significantly reduce the overall noise of the compressor by effectively attenuating noise on various frequency bands generated in the interior of the casing.

On the other hand, another embodiment of the spring cover of the present invention is as follows.

That is, in the above-described embodiment, the first spring insertion portion of the first cover and the second spring insertion portion of the second cover constituting a part of the space portion are formed substantially the same, and the first spring insertion portion 1631c and the second spring insertion portion 1632c may be formed in different shapes according to circumstances.

Fig. 11 is a sectional view showing another embodiment of the spring cover.

Referring to fig. 11, the spring cover 163 of the present embodiment may be formed of a first cover 1631 and a second cover 1632. The overall configuration and the operational effects of the first cover 1631 and the second cover 1632 are largely the same as those of the embodiment of fig. 7, and thus, a detailed description thereof will be omitted.

However, in the present embodiment, the first spring insertion portion 1631c for forming a part of the first cover 1631 and the second spring insertion portion 1632c for forming a part of the second cover 1632 may be formed differently. Thus, noise in various frequency bands can be cancelled by increasing the volume of space 163 a.

For example, since the refrigerant guiding convex portion 1631e is formed on the first spring insertion portion 1631c, there is a possibility that the length of the first spring insertion portion 1631c may be changed. On the other hand, the second spring insertion portion 1632c is formed in a closed shape, and thus has a space that can extend in the axial direction.

Accordingly, the axial length L22 of the second spring insertion part 1632c may be formed to be greater than the axial length L21 of the first spring insertion part 1631 c. However, if the axial length L22 of the second spring insertion portion 1632c is increased, the outer peripheral surface of the second spring insertion portion 1632c may interfere with the inner peripheral surface of the second spring 1622, thereby generating friction, and therefore, the second spring insertion portion 1632c may be formed in a tapered shape whose cross-sectional area is gradually reduced in a direction away from the spring support portion 1617.

Of course, in the case where the side surface of the first spring insertion portion 1632c is closed and the side surface of the second spring insertion portion 1631c is formed with a refrigerant inlet/outlet hole (not shown) and a refrigerant guide protrusion (not shown), the first spring insertion portion 1631c may be formed longer than the second spring insertion portion 1632 c. The description of the foregoing embodiments is used instead.

As described above, when the axial length L21 of the first spring insertion section 1631c and the axial length L22 of the second spring insertion section 1632c are formed to be different from each other, the volume of the space section 163a can be variously changed as necessary. Thus, noise in various frequency bands can be cancelled by the same number of spring covers 163.

On the other hand, another embodiment of the spring cover of the present invention is as follows.

That is, in the foregoing embodiment, the passage part is formed only on the first cover of the first and second covers for forming the spring cover, but the passage parts 163b1, 163b2 may be formed on the first cover 1631 and the second cover 1632, respectively, according to circumstances.

Fig. 12A to 12C are sectional views showing still another embodiment of the spring cover.

Referring to fig. 12A to 12C, the spring cover of the present embodiment may be formed of a first cover 1631 and a second cover 1632. The overall configuration and the operational effects of the first cover 1631 and the second cover 1632 are largely the same as those of the embodiment of fig. 8, and thus, a detailed description thereof will be omitted.

However, in the present embodiment, the first cover 1631 may be formed with the first passage part 163b1, and the second cover 1632 may be formed with the second passage part 163b 2. For example, a first passage part 163b1 may be formed at the first spring insertion part 1631c, and a second passage part 163b2 may be formed at the second spring insertion part 1632 c. Specifically, a first refrigerant inlet and outlet hole 1631d and a first refrigerant guiding protrusion 1631e for constituting the first channel part 163b1 may be formed at a front surface of the first spring insertion part 1631c, and a second refrigerant inlet and outlet hole 1632d and a second refrigerant guiding protrusion 1632e for constituting the second channel part 163b2 may be formed at a rear surface of the second spring insertion part 1632 c.

In this case, as shown in fig. 12A, the sectional area a21 of the first refrigerant inlet and outlet hole 1631d may be formed to be larger than the sectional area a22 of the second refrigerant inlet and outlet hole 1631 d. However, the sectional area a21 of the first refrigerant inlet and outlet hole 1631d may be formed smaller than the sectional area a22 of the second refrigerant inlet and outlet hole 1631d, or the sectional area a21 of the first refrigerant inlet and outlet hole 1631d and the sectional area a22 of the second refrigerant inlet and outlet hole 1631d may be formed to be the same.

Further, as shown in fig. 12B, the axial length L11 of the first refrigerant guiding protrusion 1631e may be formed to be greater than the axial length L12 of the second refrigerant guiding protrusion 1632 e. However, the axial length L11 of the first refrigerant guiding protrusion 1631e may be formed to be smaller than the axial length L12 of the second refrigerant guiding protrusion 1632e, or the axial length L11 of the first refrigerant guiding protrusion 1631e and the axial length L12 of the second refrigerant guiding protrusion 1632e may be formed to be the same as each other.

As described above, in the case where the first passage part 163b1 and the second passage part 163b2 are formed on both sides of the space part 163a in the axial direction, the refrigerant can be introduced into and discharged from the space part 163a via the first passage part 163b1 or can be introduced into and discharged from the space part 163a via the second passage part 163b2 in the process of the spring cover 163 reciprocating in the axial direction.

However, in this case, the refrigerant rapidly passes through space portion 163a via both side passage portions 163b1, 163b2, and the sound deadening effect may be halved. In view of this, as shown in fig. 12C, the first channel part 163b1 and the second channel part 163b2 may be formed so as to be located on lines different from each other in the axial direction. This suppresses the refrigerant flowing into space 163a via first channel 163b1 from directly flowing out to second channel 163b2, thereby improving the sound deadening effect.

On the other hand, another embodiment of the spring cover of the present invention is as follows.

That is, in the foregoing embodiment, the shapes (i.e., specifications) of all the spring caps arranged in the circumferential direction are the same, but the shapes of the respective spring caps may be formed differently depending on the circumstances.

Fig. 13A is a plan view showing the spring support member to which spring caps of different specifications are mounted, and fig. 13B to 13D are sectional views showing lines vi-vi, vi '-vi', vi "-vi" of the respective spring caps.

Referring to fig. 13A, the spring cover of the present embodiment may be formed of a first cover 1631 and a second cover 1632. The overall configuration and the operational effects of the first cover 1631 and the second cover 1632 are largely the same as those of the embodiment of fig. 8, and thus, a detailed description thereof will be omitted.

However, in the present embodiment, the shapes of the spring caps 163 adjacent in the circumferential direction may be formed differently. For example, in the case where six spring covers 163 are provided in the circumferential direction, the shapes of the respective spring covers 163 may be formed differently so that six sets of spring covers 163 may be formed, or two of them may be formed differently from each other so that three sets of spring covers 163, 163', 163 ″ may be formed.

In this case, the spring cover 163 of the first group may be formed to have a sound-deadening property on the first frequency band, and the spring cover 163' of the second group may be formed to have a sound-deadening property on the second frequency band. Further, the spring cover 163 ″ of the third group may be formed to have a sound deadening property in a third frequency band.

Here, the spring covers 163, 163', 163 ″ of the respective sets may be formed to have sound deadening properties for different frequency bands by adjusting the volume of the space portion 163a, the sectional areas a1, a2, A3 of the passage portion 163b, and the length. For example, the embodiment in fig. 11 to the embodiment in fig. 12C, and the like can be applied.

As described above, when the spring covers 163, 163', 163 ″ of the respective groups have different shapes, noise in various frequency bands generated during the driving of the compressor can be reliably canceled. Thus, the noise of various frequency bands generated in the shell is evenly offset, and the noise of the compressor can be reduced.

On the other hand, another embodiment of the spring cover of the present invention is as follows.

That is, in the foregoing embodiment, the spring cover is formed of the first cover and the second cover, and is inserted and coupled from both side surfaces of the spring support portion, but the first cover or the second cover may also penetrate and be coupled from one side surface of the spring support portion toward the other side surface thereof, according to circumstances.

Fig. 14 is a sectional view showing still another embodiment of the spring cover.

Referring to fig. 14, the spring cover 163 of the present embodiment may be formed in an elongated cylindrical shape having a hollow portion inside thereof to form a space portion 163a inside thereof.

For example, one end of the first cover 1631 may form a hole penetration part 1631f penetrating through the cover support hole 1617a of the spring support part 1617, and the other end of the first cover 1631 may form a first spring insertion part 1631c for inserting the first spring 1621. Further, in the middle of the first cover 1631, a first cover supporting portion 1631b supported by the front surface of the spring supporting portion 1617 in the axial direction may be formed.

A cover coupling portion 1632f inserted into and coupled to the hole penetration portion 1631a of the first cover 1631 may be formed at one end of the second cover 1632, and a second spring insertion portion 1632c for inserting the second spring 1622 may be formed at the other end of the second cover 1632. Further, a second cover supporting part 1632b may be formed at an outer circumferential surface of the cover coupling part 1632f, the second cover supporting part 1632b being along in a flange shape and supported to a rear surface of the spring supporting part 1617 in the axial direction.

The aforementioned passage portion 163b may be formed on at least any one of the front surface of the first spring insertion portion 1631c and the rear surface of the second spring insertion portion 1632 c. The passage portion 163b is the same as the foregoing embodiment, and thus a detailed description thereof is omitted.

As described above, when the first cover 1631 or the second cover 1632 is supported by penetrating the cover support hole 1617a of the spring support portion 1617, the first cover 1631 or the second cover 1632 can be prevented from being detached from the spring support portion 1617. Thereby, the assembling process may become easier as compared with the case where half of each of the first cover 1631 or the second cover 1632 is inserted into the cover support hole 1617 a.

On the other hand, another embodiment of the spring cover of the present invention is as follows.

That is, in the foregoing embodiment, the spring fixing protrusions are formed in the form of a sheet metal at the stator cover and the rear cover, respectively, but the spring cover may be coupled to the stator cover and the rear cover according to circumstances.

Fig. 15 is a sectional view showing another embodiment of the arrangement position of the spring cover.

Referring to fig. 15, the stator case 1611 and the rear case 1612 of the present embodiment include cover support holes 1611b and 1612c, respectively, and the spring covers 263 and 264 may be inserted into and coupled to the cover support hole 1611b of the stator case 1611 and the cover support hole 1612c of the rear case 1612, respectively.

The spring covers 263, 264 may be formed of first and second covers 2631, 2641 and 2632, 2642, respectively. The first and second lids 2631, 2641 and 2632, 2642 may be formed in the same shape as the aforementioned embodiment of fig. 8, or may be formed in other shapes as previously described. However, in the present embodiment, the springs 1621, 1622 are coupled to only one side of the spring covers 263, 264, and thus the spring insertion portion may be formed only at any one side of the first and second covers 2631, 2641, 2632, 2642.

For example, the first covers 2631 and 2641 of the present embodiment may include spring insertion portions 2631c and 2641c, respectively, which are inserted into and coupled to end portions of hole insertion portions 2632a and 2642a described later, and cover support portions 2631b and 2641b having flange shapes may be formed on outer circumferential surfaces of the spring insertion portions 2631c and 2641c, respectively, and the cover support portions 2631b and 2641b may be supported on side surfaces of the stator cover 1611 or the rear cover 1612.

Further, refrigerant inlet and outlet holes 2631d penetrating in the axial direction may be formed in side surfaces of the spring insertion portions 2631c and 2641c, refrigerant guide convex portions 2631e and 2641e extending in the axial direction may be formed around the refrigerant inlet and outlet holes 2631d, and the refrigerant guide convex portions 2631e and 2641e may be formed in a cylindrical shape along an outer periphery of the refrigerant inlet and outlet hole 2631 d. Thus, the refrigerant inlet and outlet holes 2631d and 2641d and the refrigerant guide protrusions 2631e and 2641e form the passage portions 263b and 264 b.

The second cover 2632 may include hole insertion portions 2632a and 2642a inserted through the cover support holes 1611b and 1612 c. The hole insertion portions 2632a, 2642a may be formed in a cylindrical shape in which one side thereof facing the first lids 2631, 2641 is opened and the opposite side thereof is blocked. Thus, the inner spaces formed by the hole insertion portions 2632a and 2642a of the second cover 2632 form the space portions 263a and 264 a.

As described above, in the case where the spring cover having a silencer function is provided on at least either one of the stator cover and the rear cover, the number of helmholtz resonators can be increased. This can cancel noise generated when the compressor is driven.

In this case, if the first covers 2631 and 2641 and the second covers 2632 and 2642 are formed to have different shapes, noise in various frequency bands can be cancelled.

On the other hand, another embodiment of the spring cover of the present invention is as follows.

That is, in the foregoing embodiment, the spring cover is insert-coupled to the spring support portion, but the spring cover may also be coupled between the springs according to circumstances.

Fig. 16 is a sectional view showing still another embodiment of the arrangement position of the spring cover.

Referring to fig. 16, the spring 162 of the present embodiment is disposed with a spring support portion 1617 interposed therebetween, and includes: a first spring 1621 disposed on the front side; and a second spring 1622 disposed on the rear side.

The first spring 1621 and the second spring 1622 may be divided into a plurality of springs. For example, the first spring 1621 may be divided into a front side first spring 1621a and a rear side first spring 1621b, and the second spring 1622 may be divided into a front side second spring 1622a and a rear side second spring 1622 b. Thus, the springs 162 may be arranged in the order of the front side first spring 1621a, the rear side first spring 1621b, the front side second spring 1622a, and the rear side second spring 1622b from the stator housing 1611 toward the rear housing 1612 in the axial direction.

The front end of the front side first spring 1621a may be inserted into and fixed to the first spring support protrusion 1611a of the stator housing 1611, and the rear end of the rear side first spring 1621b may be inserted into and fixed to the first cover 1631 of the spring support 1617.

In addition, a front end of the front side second spring 1622 may be inserted into and fixed to the second cover 1632 of the spring support portion 1617, and a rear end of the rear side second spring 1622 may be inserted into and fixed to the second spring support boss 1612b of the rear cover 1612.

Here, as in the above-described embodiment, the first cover 1631 and the second cover 1632 may be formed as spring covers having the space portion 163a and the passage portion 163b, or may be formed as simple spring covers having both ends opened.

However, in the present embodiment, the first spring cover 363 is provided between the front side first spring 1621 and the rear side first spring 1621, so that the front side first spring 1621 and the rear side first spring 1621 can be connected; a second spring cover 364 is provided between the front side second spring 1622 and the rear side second spring 1622 so that the front side second spring 1622 and the rear side second spring 1622 can be connected.

The first spring cover and the second spring cover may also be formed in one piece, or may also be formed by a plurality of covers as in the previously described embodiments. In fig. 15, an example in which a plurality of caps are formed is shown.

For example, the first spring cover 363 may include a front side first cover 3631 and a rear side first cover 3632.

A front side first spring insertion portion 3631a for inserting the front side first spring 1621a may be formed at one end of the front side first cover 3631, while the other end of the front side first cover 3631 may be extended in a flange shape to form a cover flange portion 3631b, the front side first spring 1621a and the rear side first spring 1621b being supported by the cover flange portion 3631b in axially opposite side directions, respectively.

A cover coupling portion 3632a inserted into and coupled to the front side first cover 3631 may be formed at one end of the rear side first cover 3632, and a rear side first spring insertion portion 3632b for inserting the rear side first spring 1621b may be formed at the other end of the rear side first cover 3632.

In this case, a first space portion 363a may be formed inside the front side first cover 3631 and the rear side first cover 3632, and a first channel portion 363b may be formed at least one side of the front side first cover 3631 and the rear side first cover 3632.

The second spring cover 364 may be formed the same as the first spring cover 363 described above. Further, the first spring cover 363 and the second spring cover 364 may be provided to be symmetrical to each other across the spring support 1617. Therefore, the description thereof is omitted.

As described above, when the first spring cover 363 is provided in the middle of the first spring 1621 and the second spring cover 364 is provided in the middle of the second spring 1622, the lateral deformation of the first spring 1621 and the second spring 1622 can be reduced, thereby suppressing the central portions of the first spring 1621 and the second spring 1622 from drooping in the lateral direction. This improves the concentricity of the piston 142, thereby reducing the friction loss between the piston 142 and the cylinder 141.

In this case, the first spring cover 363 and the second spring cover 364 are formed with the space portions 363a and 364a and the duct portions 363b and 364b, respectively, whereby the number of helmholtz resonators can be increased. Accordingly, noise generated when the compressor is driven can be offset.

In this case, if the first spring cover 363 and the second spring cover 364 are formed in different shapes, noise in various frequency bands can be cancelled.

While the present invention has been described with reference to the preferred embodiments, those skilled in the art will be able to make various modifications and alterations to the present invention without departing from the spirit and scope of the present invention as set forth in the appended claims.