阅读说明：本技术 线性压缩机 (Linear compressor ) 是由 韩聪 宋斌 朱万朋 高山 吴远刚 于 2019-09-29 设计创作，主要内容包括：本发明提供了一种线性压缩机,包括机壳；线性电机,其包括定子和动子；气缸,限定有用于压缩制冷剂的空间；活塞,在动子带动下沿线性电机的轴线方向作线性往复运动,以压缩气缸内的制冷剂；和至少一个弹簧质量减振模块,其包括连接于动子的弹性件和连接于弹性件的质量块,用于消减线性压缩机的轴向振动。本发明的线性压缩机可有效降低轴向振动,且结构简单可靠。(The invention provides a linear compressor, which comprises a shell; a linear motor including a stator and a mover; a cylinder defining a space for compressing a refrigerant; the piston is driven by the rotor to do linear reciprocating motion along the axis direction of the linear motor so as to compress a refrigerant in the cylinder; and at least one spring mass damping module including an elastic member coupled to the mover and a mass coupled to the elastic member, for damping axial vibration of the linear compressor. The linear compressor can effectively reduce axial vibration and has a simple and reliable structure.)

1. A linear compressor, characterized by comprising:

a housing;

the linear motor is arranged in the shell and comprises a stator and a rotor;

a cylinder disposed in the casing, defining a space for compressing a refrigerant;

the piston is driven by the rotor to do linear reciprocating motion along the axis direction of the linear motor so as to compress a refrigerant in the cylinder; and

at least one spring mass damping module including an elastic member connected to the mover and a mass connected to the elastic member, for damping axial vibration of the linear compressor.

2. Linear compressor according to claim 1,

the two ends of the elastic part in the length direction are respectively connected with the rotor and the mass block, and the connecting line of the two ends is not parallel to the axis direction of the linear motor.

3. Linear compressor according to claim 2,

the connecting line of the two ends of the elastic part in the length direction is vertical to the axis direction of the linear motor.

4. Linear compressor according to claim 1,

the elastic member is a plate-shaped structure made of an elastic material.

5. Linear compressor according to claim 1,

the elastic part is mounted on the rotor in a threaded connection manner; and is

The mass is mounted to the elastic member in a threaded connection.

6. Linear compressor according to claim 1,

the axial direction of the linear motor is parallel to the horizontal direction;

the stator comprises an inner stator and an outer stator which are cylindrical and coaxially arranged, the outer stator is positioned on the radial outer side of the inner stator, and an annular gap is formed between the outer stator and the inner stator;

the cylinder is positioned on one axial side of the stator;

the active cell includes annular magnet and active cell skeleton, annular magnet is located in the annular gap, the active cell skeleton is including being located stator axial opposite side and perpendicular to annular end plate portion of annular magnet axial with follow respectively the interior section of thick bamboo portion and the outer barrel portion that extend of the inside, outer periphery edge of annular end plate portion, interior section of thick bamboo portion is followed interior stator is inside to extend in order to connect in the piston, outer barrel portion connect in annular magnet.

7. Linear compressor according to claim 6,

the number of the spring mass vibration reduction modules is one, and the elastic piece is connected to the top of the inner periphery of the annular end plate part.

8. Linear compressor according to claim 6,

the number of the spring mass vibration reduction modules is one, and the elastic piece is connected to the top of the outer periphery of the annular end plate portion.

9. Linear compressor according to claim 6,

the spring mass vibration reduction modules are two in number, and the elastic pieces of the two are respectively connected to the top and the bottom of the outer periphery of the annular end plate part.

10. The linear compressor of claim 6, further comprising:

a mounting plate fixed in the housing, the annular end plate portion being located between the mounting plate and the inner stator; and

a plurality of first resonance springs and a plurality of second resonance springs all follow linear electric motor's axis direction extends, every first resonance spring both ends are fixed in respectively the mounting panel with annular end plate portion, every second resonance spring both ends are fixed in respectively annular end plate portion with the terminal surface of inner stator.

Technical Field

The invention relates to the technical field of compressors, in particular to a linear compressor.

Background

A damping spring is generally provided in the piston compressor between the bottom of the pump body and the bottom wall of the inner shell for absorbing the vibrations of the compressor.

The linear compressor is a piston type compressor to which a linear motor is applied, and the linear motor includes a stator and a mover that linearly reciprocates in an axial direction, which makes axial vibration of the linear compressor relatively large. Also, since the mover axial direction is generally parallel to the horizontal direction, this results in that the vertically extending damper springs do not have a large effect on absorbing axial vibration of the compressor.

Disclosure of Invention

An object of the present invention is to provide a linear compressor capable of effectively reducing axial vibration.

The invention further aims to reduce the axial vibration of the linear compressor and improve the reliability by using a simple and high-reliability structure.

In particular, the present invention provides a linear compressor comprising:

a housing;

the linear motor is arranged in the shell and comprises a stator and a rotor;

a cylinder disposed in the casing, defining a space for compressing a refrigerant;

the piston is driven by the rotor to do linear reciprocating motion along the axis direction of the linear motor so as to compress a refrigerant in the cylinder; and

and at least one spring mass damping module including an elastic member coupled to the mover and a mass member coupled to the elastic member, for damping axial vibration of the linear compressor.

Optionally, two ends of the elastic element in the length direction are respectively connected with the mover and the mass block, and a connection line of the two ends is not parallel to the axis direction of the linear motor.

Optionally, a line connecting two ends of the elastic member in the length direction is perpendicular to the axis direction of the linear motor.

Optionally, the resilient member is a plate-like structure made of a resilient material.

Optionally, the elastic member is mounted to the mover in a threaded manner; and the mass block is arranged on the elastic piece in a threaded connection mode.

Optionally, the axis direction of the linear motor is parallel to the horizontal direction; the stator comprises an inner stator and an outer stator which are cylindrical and coaxially arranged, the outer stator is positioned at the radial outer side of the inner stator, and an annular gap is formed between the outer stator and the inner stator; the cylinder is positioned at one axial side of the stator; the rotor comprises an annular magnet and a rotor framework, the annular magnet is positioned in the annular gap, the rotor framework comprises an annular end plate portion positioned on the other side of the axial direction of the stator and perpendicular to the axial direction of the annular magnet, an inner cylinder portion and an outer cylinder portion, the inner cylinder portion and the outer cylinder portion extend out of the inner periphery and the outer periphery of the annular end plate portion respectively, the inner cylinder portion extends from the inside of the inner stator to be connected to the piston, and the outer cylinder portion is connected to the.

Alternatively, the number of the spring-mass damper modules is one, and the elastic member is attached to the top of the inner periphery of the annular end plate portion.

Alternatively, the number of spring mass damping modules is one, and the elastic member is attached to the top of the outer periphery of the annular end plate portion.

Alternatively, the number of the spring mass damping modules is two, and the elastic members of the two are respectively connected to the top and bottom of the outer periphery of the annular end plate portion.

Optionally, the linear compressor further comprises: the mounting plate is fixed in the machine shell, and the annular end plate is positioned between the mounting plate and the inner stator; and a plurality of first resonant springs and a plurality of second resonant springs, all extend along linear electric motor's axis direction, every first resonant spring both ends are fixed in mounting panel and annular end board portion respectively, and every second resonant spring both ends are fixed in the terminal surface of annular end board portion and inner stator respectively.

The linear compressor is provided with a spring mass vibration reduction module on a rotor. In the reciprocating motion process of the rotor, the elastic part moves back and forth along with the rotor, and the mass block vibrates back and forth by taking the connection point of the elastic part and the rotor as the center due to inertia and elastic deformation of the elastic part. Therefore, the spring mass vibration reduction module changes the self-vibration characteristic of the compressor vibration system, increases the damping, absorbs the vibration energy and effectively reduces the axial vibration of the linear compressor.

Furthermore, in the linear compressor, the spring mass vibration reduction module has the advantages of simple and small structure, flexible installation position and convenient assembly, is suitable for being arranged in the linear compressor with compact structure, and does not interfere with the original structural design of the linear compressor. Moreover, the manufacturing cost is low, and the use reliability is high.

Furthermore, the number and the installation positions of the spring mass vibration attenuation modules are optimally designed, so that the vibration attenuation effect is optimal.

The above and other objects, advantages and features of the present invention will become more apparent to those skilled in the art from the following detailed description of specific embodiments thereof, taken in conjunction with the accompanying drawings.

Drawings

Some specific embodiments of the invention will be described in detail hereinafter, by way of illustration and not limitation, with reference to the accompanying drawings. The same reference numbers in the drawings identify the same or similar elements or components. Those skilled in the art will appreciate that the drawings are not necessarily drawn to scale. In the drawings:

fig. 1 is a schematic sectional view of a linear compressor according to an embodiment of the present invention;

FIG. 2 is an exploded schematic view of the spring-mass damping module of FIG. 1;

fig. 3 is a schematic sectional view of a linear compressor according to another embodiment of the present invention;

fig. 4 is a schematic sectional view of a linear compressor according to still another embodiment of the present invention.

Detailed Description

Fig. 1 is a schematic sectional view of a linear compressor according to one embodiment of the present invention. As shown in fig. 1, an embodiment of the present invention provides a linear compressor. The linear compressor may be applied to a vapor compression refrigeration cycle system, such as a refrigerator or freezer, for compressing a refrigerant.

A linear compressor of an embodiment of the present invention may generally include a casing 100, a linear motor 700, a cylinder 200, a piston 300, and at least one spring-mass damping module 500.

The casing 100 defines a receiving chamber and is mounted with a suction pipe (not shown) and a discharge pipe (not shown). The linear motor 700 is installed in the cabinet 100, and includes a stator 720 and a mover 710. The stator 720 is directly or indirectly fixed to the casing 100. When the linear motor 700 is powered on, an electromagnetic force is generated between the stator 720 and the mover 710, and the mover 710 linearly reciprocates relative to the stator 720 by the electromagnetic force.

The cylinder 200 is disposed in the casing 100, and defines a space for compressing refrigerant, i.e., a compression chamber 201. The piston 300 is driven by the mover 710 to linearly reciprocate along an axial direction of the linear motor 700 (i.e., an x-axis direction indicated in the drawing) to compress the refrigerant in the cylinder 200. The end of the cylinder 200 is also mounted with a discharge valve 210, and the piston 300 compresses the refrigerant in the cylinder 200, i.e., performs a compression process, when moving toward the discharge valve 210. When the pressure of the refrigerant gas is sufficiently high, the exhaust valve 210 is pushed open to exhaust the gas, and the exhaust process is performed. Then, the piston 300 changes its moving direction to move away from the discharge valve 210, and the cylinder 200 sucks the low-pressure refrigerant and performs a suction process. The processes of suction, compression, and exhaust of the cylinder 200 are cyclically performed.

One or more spring mass damper modules 500 are also provided on the mover 710. The spring mass damping module 500 includes an elastic member 510 and a mass 520. The elastic member 510 is connected to the mover 710, and is elastically deformed after being applied with a force, and is restored to an original state by the elastic deformation force after the external force disappears. For example, the elastic member 510 may be a plate-shaped structure made of an elastic material, such as a metal thin plate. The mass 520 is connected to a portion of the elastic member 510 such that the elastic member 510 concentrates a large mass at the portion. During the reciprocating motion of the mover 710, the elastic member 510 reciprocates with the mover 710, and the mass 520 vibrates reciprocally around the connection point of the elastic member 510 and the mover 710 due to the inertia and the elastic deformation of the elastic member 510, and the motion direction and speed of the mass 520 are not synchronized with those of the mover 710. This allows the spring mass damping module 500 to change the natural vibration characteristics of the entire vibration system of the linear compressor, and to increase damping, absorb the energy of vibration, and effectively reduce the axial vibration of the linear compressor.

Fig. 2 is an exploded schematic view of the spring-mass damping module 500 of fig. 1. As shown in fig. 1 and 2, the elastic member 510 may be long, and two ends of the elastic member in the length direction are respectively connected to the mover 710 and the mass 520, so that the center of gravity of the mass 520 is farther away from the connection point of the elastic member 510 and the mover 710, the amplitude of the mass 520 is larger, and the vibration damping capability is stronger.

The connection line of the two ends of the elastic member 510 in the length direction may be made non-parallel to the axial direction of the linear motor 700 to facilitate the deformation of the elastic member 510 and the oscillation of the mass 520. It is preferable that a line connecting both ends in a length direction of the elastic member 510 is perpendicular to an axial direction of the linear motor 700, for example, fig. 1, the axial direction of the linear motor 700 is along a horizontal direction, and the elastic member 510 is a vertically extending long bar shape, and a line connecting both ends in the length direction (i.e., upper and lower ends) is along a vertical direction. The perpendicular angle is set to optimize the deformation capability of the elastic member 510 and the swing capability of the mass 520 with respect to other angles.

As shown in fig. 2, the elastic member 510 may be threadedly mounted to the mover 710, and the mass 520 may also be threadedly mounted to the elastic member 510. Specifically, through holes 512 are formed at both ends of the elastic member 510 in the length direction, screw holes 522 are formed in the mass block 520, and the mass block 520 is connected to the elastic member 510 by screws 530. This makes installation of the spring-mass damping module 500 very convenient.

The embodiment of the invention is particularly suitable for reducing the axial vibration of the horizontal linear compressor. Figure 1 illustrates an alternative construction of a linear compressor of horizontal configuration.

As shown in fig. 1, the axial direction of the linear motor 700 is parallel to the horizontal direction. The stator 720 includes an inner stator 722 and an outer stator 721, both of which are cylindrical and coaxially disposed. The outer stator 721 is positioned radially outward of the inner stator 722 with an annular gap 701 therebetween. The inner stator 722 is provided with a coil 723. The cylinder 200 is located on one axial side of the stator 720. The mover 710 includes a ring magnet 711 and a mover frame 712. A ring magnet 711 is located in the annular gap 701 for generating electromagnetic force with the stator 720. When the linear motor 700 is powered on, the ring magnet 711 reciprocates by an electromagnetic force. The mover frame 712 includes an annular end plate portion 7122, an inner cylinder portion 7126, and an outer cylinder portion 7124. The annular end plate portion 7122 is located on the other axial side of the stator 720, that is, the annular end plate portion 7122 is aligned with the cylinder 200 and located on both axial sides of the stator 720. The plane of the annular end plate portion 7122 is perpendicular to the axial direction (x-axis) of the ring magnet 711. An inner cylinder portion 7126 and an outer cylinder portion 7124 extend from inner and outer peripheries of the annular end plate portion 7122, respectively, and the inner cylinder portion 7126 extends from a central through hole 702 inside the inner stator 722 to the piston 300 and is connected to the piston 300 for driving the piston 300. The outer cylinder portion 7124 is connected to the ring magnet 711. The annular end plate portion 7122, the inner cylinder portion 7126 and the outer cylinder portion 7124 may be formed integrally or may be assembled.

As shown in fig. 1, a skeleton 900 may also be provided. The frame 900 is fixed in the casing 100 to fix the stator 720 and the cylinder 200. The stator 720 and the cylinder 200 are directly or indirectly fixed to the frame 900. For example, the cylinder 200 may be indirectly secured to the frame 900 via a flange 220. The flange 220 is secured within the framework 900 and has an internal bore. One axial end of the flange 220 abuts against one axial end of the stator 720, and the other axial end abuts against the inside of the end plate 920 of the bobbin 900. The cylinder 200 is fixed in the inner hole of the flange 220. The end plate 920 has a discharge chamber 932 at the middle for accommodating the discharge valve 210, and the end plate 920 is externally provided with an end cap 930 for closing the discharge chamber 932. The linear compressor may have a low back pressure structure, the cylinder 200 sucks a low pressure refrigerant from the inside of the casing 100, and the discharge airflow of the compression chamber 201 communicates with the discharge pipe of the casing 100 to discharge a high pressure gas. In some alternative embodiments, the linear compressor may also be of a medium-back pressure or high-back pressure structure, and the specific arrangement is well known to those skilled in the art and will not be described herein.

Fig. 3 is a schematic sectional view of a linear compressor according to another embodiment of the present invention; fig. 4 is a schematic sectional view of a linear compressor according to still another embodiment of the present invention.

Fig. 1, 3 and 4 illustrate several preferred mounting positions of the spring-mass damping module 500. According to the embodiment of the invention, the number and the installation positions of the spring mass damping modules 500 are optimally designed, so that the axial damping effect is optimal.

In some embodiments, as shown in fig. 1, the number of spring-mass damper modules 500 is one. Also, the elastic member 510 is attached to the top of the inner peripheral edge of the annular end plate portion 7122. Specifically, the elastic member 510 is a long plate structure, and has an upper end connected to the annular end plate portion 7122 and a lower end connected to the mass 520. The lower end of the elastic member 510 is opposite to the cavity of the inner cylinder portion 7126 to facilitate the vibration of the elastic member 510.

In some embodiments, as shown in fig. 2, the number of spring-mass damper modules 500 is one. Also, an elastic member 510 is attached to the top of the outer periphery of the ring-shaped end plate portion 7122. Specifically, the elastic member 510 is a long plate-shaped structure, and has a lower end connected to the annular end plate portion 7122 and an upper end connected to the mass 520, so that the mass 520 is located higher than the outer cylinder portion 7124.

In some embodiments, as shown in fig. 3, the number of spring-mass damper modules 500 is two. Also, the elastic members 510 of the two spring mass damper modules 500 are connected to the top and bottom of the outer periphery of the ring-shaped end plate portion 7122, respectively. In particular, the elastic members 510 of both spring-mass damper modules 500 are of an elongated plate-like structure. The elastic member 510 of the spring-mass damping module 500 located at the upper side has a lower end connected to the ring-shaped end plate portion 7122 and an upper end connected to the mass 520, so that the mass 520 is located higher than the outer cylinder portion 7124 to facilitate the vibration thereof. The elastic member 510 of the spring mass damping module 500 at the lower side is connected at the upper end to the ring-shaped end plate portion 7122 and at the lower end to the mass 520 so that the mass 520 is positioned lower than the outer cylindrical portion 7124 to facilitate its vibration.

In addition to the above three optimal setting schemes, other reasonable designs can be performed on the number and the installation positions of the spring mass damping modules 500, so that the spring mass damping modules can achieve the effect of damping axial vibration.

In the linear compressor of the embodiment of the invention, the spring mass vibration reduction module 500 has the advantages of simple and small structure, flexible installation position, convenient assembly and high reliability, is suitable for being arranged in the compressor with compact structure, and does not interfere with the original structural design of the compressor. Moreover, the cost is very low.

In some embodiments, as shown in fig. 1, the linear compressor further comprises a resonant system. Specifically, the mounting plate 400, a plurality of first resonant springs 810, and a plurality of second resonant springs 820 are included.

The mounting plate 400 is fixed in the cabinet 100, and the ring-shaped end plate portion 7122 is positioned between the mounting plate 400 and the inner stator 722. Each of the plurality of first resonant springs 810 and the plurality of second resonant springs 820 extends in the axial direction of the linear motor 700. Both ends of each first resonant spring 810 are fixed to the mounting plate 400 and the ring-shaped end plate portion 7122, respectively, and both ends of each second resonant spring 820 are fixed to the end faces of the ring-shaped end plate portion 7122 and the inner stator 722, respectively.

When the linear compressor is operated, the resonant spring, the mover 720 and the piston 300 form a vibration system, and when the operation frequency of the linear compressor reaches or approaches to the resonance frequency of the vibration system, the linear compressor can obtain higher energy efficiency, and the vibration and noise of the compressor can be lower. Resonant systems are widely used in linear compressors and the principle thereof will not be described too much here.

It is preferable that the number of the first resonant springs 810 and the second resonant springs 820 is the same, for example, 10. And, each of the first resonant springs 810 is coaxially disposed with one of the second resonant springs 820. Further, the plurality of first resonant springs 810 and the plurality of second resonant springs 820 may be uniformly distributed on a circumference (i.e., with the x-axis as a central axis) coaxial with the linear motor 700. Thus, the resonant springs support the mover 710 more uniformly and dispersedly, and unnecessary deformation of the resonant springs and unnecessary vertical displacement of the mover 710 are reduced, so that the movement of the mover is more accurate.

The embodiment shown in fig. 1 provides only two sets of resonant springs, and in some alternative embodiments, three or more sets of resonant springs may be provided.

Thus, it should be appreciated by those skilled in the art that while a number of exemplary embodiments of the invention have been illustrated and described in detail herein, many other variations or modifications consistent with the principles of the invention may be directly determined or derived from the disclosure of the present invention without departing from the spirit and scope of the invention. Accordingly, the scope of the invention should be understood and interpreted to cover all such other variations or modifications.