阅读说明：本技术 涡旋式压缩机 (Scroll compressor having a discharge port ) 是由 李卿在 徐祯基 于 2020-03-26 设计创作，主要内容包括：本发明的涡旋式压缩机包括：外壳；马达,设置在上述外壳的内部；旋转轴,通过上述马达进行旋转；回旋式涡旋盘,与上述旋转轴联动进行回旋运动；以及固定式涡旋盘,与上述回旋式涡旋盘一同形成压缩室,上述外壳包括：中心外壳,使上述旋转轴贯通；前外壳,形成有用于收容上述马达的马达收容空间；排出室,用于收容从上述压缩室排出的制冷剂；排出口,用于向上述外壳的外部引导上述排出室的制冷剂；导入口,从上述外壳的外部导入中间压力的制冷剂；以及后外壳,形成有导入室,上述导入室用于收容通过上述导入口导入的制冷剂,上述固定式涡旋盘可包括注入口,用于向上述压缩室引导上述导入室的制冷剂。由此,可通过增加从压缩室排出的制冷剂排出量来提高压缩机的性能及效率。(The scroll compressor of the present invention includes: a housing; a motor disposed inside the housing; a rotating shaft rotated by the motor; a rotary scroll which is linked with the rotating shaft to perform a rotary motion; and a fixed scroll forming a compression chamber together with the orbiting scroll, the housing including: a center housing through which the rotating shaft passes; a front housing formed with a motor receiving space for receiving the motor; a discharge chamber for receiving the refrigerant discharged from the compression chamber; a discharge port for guiding the refrigerant in the discharge chamber to the outside of the housing; an inlet port for introducing a refrigerant of an intermediate pressure from the outside of the casing; and a rear casing having an introduction chamber for receiving the refrigerant introduced through the introduction port, wherein the fixed scroll may include an injection port for guiding the refrigerant of the introduction chamber to the compression chamber. Thus, the performance and efficiency of the compressor can be improved by increasing the discharge amount of the refrigerant discharged from the compression chamber.)

1. A scroll compressor is characterized in that,

the method comprises the following steps:

a housing;

a motor disposed inside the housing;

a rotating shaft rotated by the motor;

a rotary scroll that rotates in conjunction with the rotary shaft; and

a fixed scroll forming a compression chamber together with the orbiting scroll,

the above-mentioned shell includes:

a center housing through which the rotating shaft passes;

a front housing formed with a motor receiving space for receiving the motor;

a discharge chamber for receiving the refrigerant discharged from the compression chamber;

a discharge port for guiding the refrigerant in the discharge chamber to the outside of the housing;

an inlet port for introducing a refrigerant of an intermediate pressure from the outside of the casing; and

a rear housing having an introduction chamber for receiving the refrigerant introduced through the introduction port,

the fixed scroll includes an inlet for introducing the refrigerant in the introduction chamber into the compression chamber.

2. The scroll compressor of claim 1, wherein the rear housing is formed as one piece.

3. The scroll compressor according to claim 1, wherein at least a portion of the introduction chamber is accommodated in the discharge chamber.

4. The scroll compressor of claim 3, wherein the rear housing includes:

a first annular wall fastened to the center housing and having a scroll accommodating space for accommodating the orbiting scroll and the fixed scroll;

a second annular wall which is accommodated in the first annular wall and forms the discharge chamber; and

and a third annular wall which is accommodated in the second annular wall and forms the introduction chamber.

5. The scroll compressor of claim 4, wherein the first annular wall, the second annular wall, and the third annular wall have different heights from one another.

6. The scroll compressor of claim 4,

the second annular wall is in contact with the outer peripheral portion of the fixed hard plate of the fixed scroll,

when the rear shell is fastened to the center shell, the second annular wall presses the fixed scroll toward the center shell.

7. The scroll compressor of claim 4, wherein the third annular wall is formed spaced from the fixed scroll.

8. The scroll compressor according to claim 7, wherein an injection valve assembly is formed at a front end surface of the third annular wall to communicate with and block a space between the introduction chamber and the injection port.

9. The scroll compressor of claim 8, wherein the injection valve assembly comprises:

a cover plate having an inlet communicating with the introduction chamber and covering the introduction chamber;

an injection valve for opening and closing the inflow port; and

and a valve plate serving as a retainer of the injection valve, the valve plate having an inclined space for receiving the refrigerant flowing in through the inlet port and an outlet port for guiding the refrigerant in the inclined space to the inlet port.

10. The scroll compressor of claim 8,

the fixed scroll includes a discharge port for discharging the refrigerant of the compression chamber to the discharge chamber,

a discharge valve for opening and closing the discharge port is formed between the injection valve assembly and the fixed scroll.

11. The scroll compressor according to claim 8, wherein the refrigerant introduced to the injection port is heat-exchanged with the refrigerant of the discharge chamber through the third annular wall and the injection valve assembly.

12. The scroll compressor according to claim 1, wherein at least a portion of the discharge port is accommodated in the introduction chamber.

13. The scroll compressor according to claim 12, wherein the refrigerant in the introduction chamber exchanges heat with the refrigerant in the discharge port by being accommodated in a wall portion of the discharge port of the introduction chamber.

14. The scroll compressor according to claim 1, wherein at least a part of the introduction port is accommodated in the discharge chamber.

15. The scroll compressor according to claim 14, wherein the refrigerant of the inlet port exchanges heat with the refrigerant of the discharge chamber through a wall portion of the inlet port accommodated in the discharge chamber.

Technical Field

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of compressing a refrigerant by a fixed scroll and a orbiting scroll.

Background

Generally, an automobile is equipped with an Air Conditioning unit (a/C) for cooling the interior of the automobile. Such an air conditioner includes, as a structure in a refrigeration system, a compressor that feeds a condenser by compressing a low-temperature, low-pressure gas-phase refrigerant introduced from an evaporator into a high-temperature, high-pressure gas-phase refrigerant.

The compressor is classified into a reciprocating type compressing a refrigerant based on a reciprocating motion of a piston and a rotary type performing compression by a rotary motion. The reciprocating type is classified into a crank type in which power is transmitted to a plurality of pistons using a crank according to a transmission method of a driving source, a swash plate type in which power is transmitted to a shaft provided with a swash plate, and the rotary type is classified into a vane rotary type using a rotating disc shaft and vanes, and a scroll type using a orbiting scroll and a fixed scroll.

The scroll compressor can obtain a relatively high compression ratio compared to other kinds of compressors, make suction, compression, and discharge strokes of refrigerant soft and engaged, and obtain a stable torque, and is widely used for refrigerant compression in air conditioners and the like due to such advantages.

Fig. 1 is a sectional view illustrating a conventional scroll compressor.

Referring to fig. 1, a conventional scroll compressor includes: a housing 100; a motor 200 disposed inside the casing 100; a rotation shaft 300 rotated by the motor 200; a orbiting scroll 400 which performs a orbiting motion in conjunction with the rotating shaft 300; and a fixed scroll 500 forming a compression chamber C together with the orbiting scroll 400,

in the conventional scroll compressor having the above-described configuration, when power is applied to the motor 200, the rotary shaft 300 rotates together with the rotor of the motor 200, the orbiting scroll 400 performs an orbiting motion in conjunction with the rotary shaft 300, and refrigerant is repeatedly sucked into the compression chamber C and compressed in the compression chamber C by the orbiting motion of the orbiting scroll 400, and is discharged from the compression chamber C.

However, such a conventional scroll compressor has a problem in that the amount of refrigerant discharged from the compressor C is a fixed amount, and therefore, the improvement of the performance and efficiency of the compressor is limited.

Disclosure of Invention

Accordingly, an object of the present invention is to provide a scroll compressor capable of improving the performance and efficiency of the compressor by increasing the discharge amount of refrigerant discharged from a compression chamber.

In order to achieve the above object, the present invention provides a scroll compressor including: a housing; a motor disposed inside the housing; a rotating shaft rotated by the motor; a rotary scroll that rotates in conjunction with the rotary shaft; and a fixed scroll forming a compression chamber together with the orbiting scroll, the housing including: a center housing through which the rotating shaft passes; a front housing formed with a motor receiving space for receiving the motor; a discharge chamber for receiving the refrigerant discharged from the compression chamber; a discharge port for guiding the refrigerant in the discharge chamber to the outside of the housing; an inlet port for introducing a refrigerant of an intermediate pressure from the outside of the casing; and a rear housing having an introduction chamber for receiving the refrigerant introduced through the introduction port, wherein the fixed scroll includes an injection port for introducing the refrigerant of the introduction chamber into the compression chamber.

The rear case may be formed in one body.

At least a part of the introduction chamber may be accommodated in the discharge chamber.

The rear case may include: a first annular wall fastened to the center housing and having a scroll accommodating space for accommodating the orbiting scroll and the fixed scroll; a second annular wall which is accommodated in the first annular wall and forms the discharge chamber; and a third annular wall which is accommodated in the second annular wall and forms the introduction chamber.

The first annular wall, the second annular wall, and the third annular wall may have different heights from each other.

The second annular wall is in contact with an outer peripheral portion of a fixed hard plate of the fixed scroll, and when the rear housing is fastened to the center housing, the second annular wall can apply pressure to the fixed scroll toward the center housing.

The third annular wall may be formed spaced apart from the fixed scroll.

An injection valve assembly may be formed on a front end surface of the third annular wall to communicate with and block a space between the introduction chamber and the injection port.

The above-mentioned injection valve assembly may include: a cover plate having an inlet communicating with the introduction chamber and covering the introduction chamber; an injection valve for opening and closing the inflow port; and a valve plate serving as a retainer of the injection valve, the valve plate having an inclined space for receiving the refrigerant flowing in through the inlet port and an outlet port for guiding the refrigerant in the inclined space to the inlet port.

The fixed scroll may include a discharge port for discharging the refrigerant of the compression chamber to the discharge chamber, and a discharge valve for opening and closing the discharge port may be formed between the injection valve assembly and the fixed scroll.

The refrigerant introduced to the injection port may exchange heat with the refrigerant in the discharge chamber through the third annular wall and the injection valve assembly.

At least a part of the discharge port may be accommodated in the introduction chamber.

The refrigerant in the introduction chamber can exchange heat with the refrigerant at the discharge port by being accommodated in a wall portion of the discharge port of the introduction chamber.

At least a part of the introduction port may be accommodated in the discharge chamber.

The refrigerant at the inlet port can exchange heat with the refrigerant in the discharge chamber by being accommodated in a wall portion of the inlet port of the discharge chamber.

The scroll compressor of the present invention includes: a housing; a motor disposed inside the housing; a rotating shaft rotated by the motor; a rotary scroll which is linked with the rotating shaft to perform a rotary motion; and a fixed scroll forming a compression chamber together with the orbiting scroll, the housing including: a center housing through which the rotating shaft passes; a front housing formed with a motor receiving space for receiving the motor; a discharge chamber for receiving the refrigerant discharged from the compression chamber; a discharge port for guiding the refrigerant in the discharge chamber to the outside of the housing; an inlet port for introducing a refrigerant of an intermediate pressure from the outside of the casing; and a rear shell having an introduction chamber for receiving the refrigerant introduced through the introduction port, wherein the fixed scroll includes an injection port for guiding the refrigerant of the introduction chamber to the compression chamber, thereby increasing a refrigerant discharge amount discharged from the compression chamber to improve performance and efficiency of the compressor.

Drawings

Fig. 1 is a sectional view illustrating a conventional scroll compressor.

Fig. 2 is a sectional view illustrating a scroll compressor according to an embodiment of the present invention.

Fig. 3 is a sectional view showing a rear shell side in the scroll compressor of fig. 2 in another direction.

Fig. 4 is a cross-sectional view showing a portion a of fig. 3 in an enlarged manner.

Fig. 5 is a front view illustrating a rear housing in the scroll compressor of fig. 2.

Fig. 6 is a rear view of fig. 5.

Fig. 7 is a perspective view of fig. 6.

Fig. 8 is an exploded perspective view illustrating a plurality of components housed in the rear case of fig. 7.

Fig. 9 is an exploded perspective view illustrating an injection valve assembly among components of fig. 8.

Fig. 10 is a perspective view illustrating a rear surface of a cap plate in the injection valve assembly of fig. 9.

Fig. 11 is a perspective view showing a back surface of a valve plate in the injection valve assembly of fig. 9.

Fig. 12 is a perspective view taken along line I-I of fig. 9.

Fig. 13 is a front view showing a fixed scroll and a discharge valve among the components of fig. 8.

Fig. 14 is a rear view of fig. 13.

Fig. 15 is a perspective view taken along line ii-ii of fig. 13.

Fig. 16 is a cross-sectional view illustrating the fixed wrap, the orbiting wrap, and the injection port when a rotation angle of the rotation shaft is a first angle in order to explain an opening and closing operation of the injection port of fig. 13.

Fig. 17 is a sectional view illustrating the fixed wrap, the orbiting wrap, and the injection port when the rotation angle of the rotation shaft is a second angle in order to explain the opening and closing operation of the injection port of fig. 13.

Fig. 18 is a sectional view illustrating the fixed wrap, the orbiting wrap, and the injection port when a rotation angle of the rotation shaft is a third angle in order to explain an opening and closing operation of the injection port of fig. 13.

Fig. 19 is a sectional view illustrating the fixed wrap, the orbiting wrap, and the injection port when a rotation angle of the rotation shaft is a fourth angle in order to explain an opening and closing operation of the injection port of fig. 13.

Fig. 20 is a graph showing opening and closing times of the injection port of fig. 13.

Fig. 21 is an exploded perspective view illustrating an injection valve assembly in a scroll compressor according to another embodiment of the present invention.

Fig. 22 is a plan view illustrating the injection valve and the valve plate of fig. 21.

Fig. 23 is a cross-sectional view taken along line iii-iii of fig. 22.

FIG. 24 is a cross-sectional view taken along line IV-IV of FIG. 22.

Detailed Description

Hereinafter, a scroll compressor according to the present invention will be described in detail with reference to the accompanying drawings.

Fig. 2 is a sectional view illustrating a scroll compressor according to an embodiment of the present invention, fig. 3 is a sectional view illustrating a rear shell side in the scroll compressor of fig. 2 in another direction, and fig. 4 is a sectional view illustrating a portion a of fig. 3 in an enlarged manner. Fig. 5 is a front view illustrating a rear housing in the scroll compressor of fig. 2, fig. 6 is a rear view of fig. 5, fig. 7 is a perspective view of fig. 6, which is a perspective view illustrating a portion of the rear housing in a cutaway manner, fig. 8 is an exploded perspective view illustrating a plurality of components housed in the rear housing of fig. 7, fig. 9 is an exploded perspective view illustrating an injection valve assembly among the plurality of components of fig. 8, fig. 10 is a perspective view illustrating a rear surface of a cover plate in the injection valve assembly of fig. 9, fig. 11 is a perspective view illustrating a rear surface of a valve plate in the injection valve assembly of fig. 9, fig. 12 is a perspective view taken along line I-I of fig. 9, fig. 13 is a front view illustrating a fixed scroll and a discharge valve among the plurality of components of fig. 8, fig. 14 is a rear view of fig. 13, and fig. 15 is a perspective view taken along line ii-ii of fig. 13.

Fig. 16 to 19 are sectional views for explaining opening and closing operations of the injection port of fig. 13, fig. 16 is a sectional view showing the fixed wrap, the orbiting wrap, and the injection port when the rotation angle of the rotary shaft is a first angle, fig. 17 is a sectional view showing the fixed wrap, the orbiting wrap, and the injection port when the rotation angle of the rotary shaft is a second angle, fig. 18 is a sectional view showing the fixed wrap, the orbiting wrap, and the injection port when the rotation angle of the rotary shaft is a third angle, and fig. 19 is a sectional view showing the fixed wrap, the orbiting wrap, and the injection port when the rotation angle of the rotary shaft is a fourth angle.

Fig. 20 is a graph showing opening and closing times of the injection port of fig. 13.

Referring to fig. 2 to 20, a scroll compressor according to an embodiment of the present invention may include: a housing 100, a motor 200 disposed inside the housing 100; a rotation shaft 300 rotated by the motor 200; a orbiting scroll 400 which performs a orbiting motion in conjunction with the rotating shaft 300; and a fixed scroll 500 forming a compression chamber C together with the orbiting scroll 400.

Also, the scroll compressor of the present embodiment may further include: an injection flow path for introducing an intermediate-pressure refrigerant from the outside of the casing 100 (for example, below the condenser in a vapor compression refrigeration cycle system including a scroll compressor, a condenser, an expansion valve, and an evaporator) to the compression chamber C; and an injection valve assembly 700 for opening and closing the injection flow path.

The injection flow path may include an inlet 133, an introduction chamber I, an inlet 712, an inclined space 734, a connection flow path 738, an outlet 736, and an inlet 514, which will be described later, and may be formed to extend from the rear housing 130 to the fixed scroll 500, and the injection valve assembly 700 may include an inlet 712, an inclined space 734, a connection flow path 738, and an outlet 736, which will be described later, and may be formed between the rear housing 130 and the fixed scroll 500.

Specifically, as shown in fig. 2, the housing 100 may include: a center housing 110 through which the rotary shaft 300 passes; a front housing 120 having a motor receiving space S1 for receiving the center housing 110 and the motor 200 together; and a rear housing 130 having a scroll accommodating space S2 for accommodating the center housing 110, the orbiting scroll 400, and the fixed scroll 500 together.

The center housing 110 may include: a center hard plate 112 for dividing the motor accommodating space S1 and the scroll accommodating space S2 and supporting the orbiting scroll 400 and the fixed scroll 500; and a center side plate 114 formed to protrude from an outer circumferential portion of the center hard plate 112 toward the front case 120 side.

The central hard plate 112 may have a substantially disk shape, and the central portion of the central hard plate 112 may include: a bearing hole 112a through which one end of the rotary shaft 300 passes; and a back pressure chamber 112b for applying pressure to the orbiting scroll 400 toward the fixed scroll 500. An eccentric bushing 310 may be formed at one end of the rotary shaft 300 to convert the rotation of the rotary shaft 300 into the swirling motion of the orbiting scroll 400, and the back pressure chamber 112b may provide a space in which the eccentric bushing 310 can rotate.

As described below, a suction flow path (not shown) may be formed in the outer peripheral portion of the center hard plate 112 to guide the refrigerant flowing into the motor accommodating space S1 to the scroll accommodating space S2.

The front case 120 may include: a front hard plate 122 facing the center hard plate 122 and supporting the other end of the rotary shaft 300; and a front side plate 124 protruding from an outer peripheral portion of the front hard plate 122, fastened to the center side plate 114, and supporting the motor 200.

The center hard plate 122, the center side plate 114, the front hard plate 122, and the front side plate 124 may form the motor accommodating space S1.

A suction port (not shown) for introducing a refrigerant of a suction pressure from the outside into the motor accommodating space S1 may be formed in the front plate 124.

As shown in fig. 2, 3, and 5 to 8, the rear housing 130 includes: a discharge chamber D for accommodating the refrigerant discharged from the compression chamber C; a discharge port 131 for guiding the refrigerant in the discharge chamber D to the outside of the casing 100; an inlet 133 for introducing a refrigerant of an intermediate pressure from the outside of the casing 100; and an introduction chamber I for accommodating the refrigerant introduced through the introduction port 133, wherein at least a part of the introduction chamber I is accommodated in the discharge chamber D, at least a part of the discharge port 131 is accommodated in the introduction chamber I, and at least a part of the introduction port 133 is accommodated in the discharge chamber D.

Specifically, the rear case 130 includes: a rear hard plate 132 facing the center hard plate 112; a first annular wall 134 projecting from the rear hard plate 132 and located on the outermost peripheral side in the circumferential direction of the rear housing 130; a second annular wall 136 protruding from the rear hard plate 132 and housed in the first annular wall 134; and a third annular wall 138 protruding from the rear hard plate 132 and received in the second annular wall 136, wherein the first annular wall 134, the second annular wall 136, and the third annular wall 138 may have different heights.

The first annular wall 134 may have a ring shape having a diameter substantially equal to a horizontal diameter of the outer peripheral portion of the center hard plate 112, and may be fastened to the outer peripheral portion of the center hard plate 112 to form the scroll receiving space S2.

The second annular wall 136 may have a smaller diameter than the first annular wall 134, and may be in contact with an outer circumferential portion of a fixed hard plate 510, which will be described later, to form the discharge chamber D.

The second annular wall 136 may be in contact with a fixed hard plate 510, which will be described later, and when the rear housing 130 is fastened to the center housing 110, a fastening force between the fixed scroll 500 and the center housing 110 is increased by applying pressure to the center housing 110 side to increase the fastening force between the fixed scroll 500 and the center housing 110, thereby preventing leakage between the fixed scroll 500 and the center housing 110.

The third annular wall 138 may be formed in an annular shape having a smaller diameter than the second annular wall 136, and may be covered with a cover plate 710, which will be described later, so as to be spaced apart from the fixed hard plate 510, which will be described later, thereby forming the introduction chamber I.

Moreover, the third annular wall 138 may include: a fastening groove 138a into which a fastening bolt 770 is inserted, the fastening bolt 770 fastening the injection valve assembly 700 to the third annular wall 138; and a first positioning groove 138b into which a positioning pin 780 is inserted, the positioning pin 780 being used to align a cover plate 710, a fill valve 720, and a valve plate 730, which will be described later, at predetermined positions.

The discharge port 131 may be formed in the rear hard plate 132, and the discharge port 131 may be formed to extend from a center portion of the rear hard plate 132 toward an outer peripheral portion side of the rear hard plate 132 in a radial direction of the rear hard plate 132.

A discharge inlet 131a for guiding the refrigerant in the discharge chamber D to the discharge port 131 may be formed in the rear hard plate 132.

On the other hand, a pipe-shaped oil separator (not shown) for separating oil from the refrigerant may be provided inside the discharge port 131, and the oil separator (not shown) may separate the refrigerant flowing into the discharge inlet 131a from the oil while flowing toward the center of the rear hard plate 132 along a space between the outer circumferential surface of the oil separator (not shown) and the inner circumferential surface of the discharge port 131 and then being discharged toward the outer circumferential portion of the rear hard plate 132 along the inner circumferential portion of the oil separator (not shown) by turning.

The inlet 133 may be formed in the rear hard plate 132, and the inlet 133 may extend from the other side of the outer peripheral portion of the rear hard plate 132 toward the central portion of the rear hard plate 132 along the radial direction of the rear hard plate 132 and may communicate with the inlet chamber I.

Here, as the third annular wall 138 is received in the second annular wall 136, and the third annular wall 138 is covered by the injection valve assembly 700 while being spaced apart from the fixed hard plate 510, which will be described later, at least a part of the introduction chamber I may be received in the discharge chamber D. That is, a side portion of the introduction chamber I may overlap the discharge chamber D in the radial direction of the rear housing 130 through the third annular wall 138, and a front end portion of the introduction chamber I may overlap the discharge chamber D in the axial direction of the rear housing 130 through the injection valve assembly 700.

Further, the discharge port 131 may be formed to extend in a radial direction of the rear hard plate 132 from a center portion of the rear hard plate 132 toward an outer peripheral portion side of the rear hard plate 132, and at least a portion of the discharge port 131 may be accommodated in the introduction chamber I. That is, at least a part of the discharge port 131 may overlap the introduction chamber I along the axial direction of the rear housing 130 with the wall of the discharge port 131 interposed therebetween.

Further, the introduction port 133 may be formed to extend in the radial direction of the rear hard plate 132 from the other side of the outer peripheral portion of the rear hard plate 132 toward the center portion of the rear hard plate 132, and at least a part of the introduction port 133 may be accommodated in the discharge chamber D. That is, at least a part of the introduction port 133 may overlap the discharge chamber D in the axial direction of the rear housing 130 with the wall of the introduction port 133 interposed therebetween.

On the other hand, the discharge port 131 and the introduction port 133 can allow the refrigerant at the discharge port 131 and the refrigerant at the introduction port 133 to flow in directions intersecting each other. That is, an angle between the outlet of the discharge port 131 and the inlet of the introduction port 133 may be 0 degree or more and less than 90 degrees with respect to the center of the rear case 130.

As shown in fig. 2, the motor 200 may include: a stator 210 fixed to the front plate 124; and a rotor 220 rotating inside the stator 210 by interaction with the stator 210.

As shown in fig. 2, the rotary shaft 300 may be fastened to the rotor 220 and penetrate through the center of the rotor 220, such that one end of the rotary shaft 300 penetrates through the bearing hole 112a of the center hard plate 112 and the other end of the rotary shaft 300 is supported by the front hard plate 122.

As shown in fig. 2, 16 to 19, the above-mentioned orbiting scroll 400 may include: a hard rotating plate 410 formed between the central hard plate 112 and the fixed scroll 500 and having a disk shape; a orbiting scroll 420 protruding from a central portion of the orbiting hard plate 410 toward the fixed scroll 500; and a boss portion 430 protruding from a central portion of the orbiting hard plate 410 toward the opposite side of the orbiting scroll 420 and fastened to the eccentric bush 310.

As shown in fig. 2 to 4, 8, and 13 to 19, the fixed scroll 500 may include: a fixed hard plate 510 in the shape of a disc; a fixed scroll 520 protruding from a central portion of the fixed hard plate 510 and engaged with the orbiting scroll 420; and a fixed side plate 530 protruding from an outer circumferential portion of the fixed hard plate 510 and fastened to the central hard plate 112.

The fixing hard plate 510 may include: a discharge port 512 for discharging the refrigerant in the compression chamber C to the discharge chamber D; and an injection port 514 for introducing the refrigerant discharged from the injection valve assembly 700 into the compression chamber C;

the discharge port 512 may be formed in plural to prevent the refrigerant from being excessively compressed, and the discharge ports 512 may be opened or closed by a discharge valve 600 formed between the fixing hard plate 510 and the injection valve assembly 700.

Specifically, the compression chamber C may include: a first compression chamber C1 located at the center side in the radial direction of the scroll accommodating space S2 and having a refrigerant pressure in a first pressure range; a second compression chamber C2 located on the radial center side of the scroll accommodating space S2 with respect to the first compression chamber C1 and having a refrigerant pressure in a second pressure range higher than the first pressure range; and a third compression chamber C3 located on the radial center side of the scroll accommodating space S2 with respect to the second compression chamber C2, the refrigerant pressure being in a third pressure range higher than the second pressure range, and a pair of the first compression chamber C1, the second compression chamber C2, and the third compression chamber C3 may be formed.

That is, the first compression chamber C1 may include: a first outer compression chamber C11 formed by the outer circumferential surface of the orbiting scroll 420 and the inner circumferential surface of the fixed scroll 520; and a first inner compression chamber C12 formed by an inner circumferential surface of the orbiting scroll 420 and an outer circumferential surface of the fixed scroll 520.

Also, the second compression chamber C2 may include: a second outer compression chamber C21 formed by the outer circumferential surface of the orbiting scroll 420 and the inner circumferential surface of the fixed scroll 520; and a second inner compression chamber C22 formed by an inner circumferential surface of the orbiting scroll 420 and an outer circumferential surface of the fixed scroll 520.

Also, the third compression chamber C3 may include: a third outer compression chamber C31 formed by the outer circumferential surface of the orbiting scroll 420 and the inner circumferential surface of the fixed scroll 520; and a third inner compression chamber C32 formed by an inner circumferential surface of the orbiting scroll 420 and an outer circumferential surface of the fixed scroll 520.

In this case, the discharge port 512 may include: a main discharge port 512a formed at a center side of the fixed hard plate 510, for discharging the refrigerant of the third outer compression chamber C31 and the third inner compression chamber C32; a first sub-discharge port 512b formed radially outward of the fixed hard plate 510 with reference to the main discharge port 512a, for discharging the refrigerant of the second outer compression chamber C21; and a second sub discharge port 512C formed radially outward of the fixed hard plate 510 with respect to the main discharge port 512a and formed opposite to the first sub discharge port 512b with respect to the main discharge port 512a to discharge the refrigerant of the second inner compression chamber C22.

Also, the discharge valve 600 may include: a main opening/closing part 610 for opening or closing the main discharge port 512 a; a first sub opening/closing part 630 for opening or closing the first sub discharge port 512 b; a second sub opening/closing part 650 for opening or closing the second sub discharge port 512 c; a fastening portion 670 fastened to the fixed hard plate 510; a main supporting part 620 extending from the main opening/closing part 610 to the fastening part 670; a first sub-supporting part 640 extending from the first sub-opening and closing part 630 to the fastening part 670; and a second sub supporting part 660 extending from the second sub opening/closing part 650 to the fastening part 670.

The main opening/closing unit 610 may open the main discharge port 512a when the pressures of the third outer compression chamber C31 and the third inner compression chamber C32 reach the discharge pressure level, the first sub opening/closing unit 630 may open the first sub discharge port 512b to reduce the pressure of the second outer compression chamber C21 to the level of the second pressure range when the pressure of the second outer compression chamber C21 is greater than the second pressure range, and the second sub opening/closing unit 650 may open the second sub discharge port 512C to reduce the pressure of the second inner compression chamber C22 to the level of the second pressure range when the pressure of the second inner compression chamber C22 is greater than the second pressure range, thereby preventing the pressure of the refrigerant discharged from the main discharge port 512a from being excessively higher than the discharge pressure. That is, excessive compression can be prevented.

On the other hand, the first sub discharge port 512b and the second sub discharge port 512C may communicate with the second outer compression chamber C21 and the second inner compression chamber C22 at the same time, so as to prevent pressure unevenness from occurring between the second outer compression chamber C21 and the second inner compression chamber C22. That is, when the first sub discharge port 512b communicates with the second outer compression chamber C21, the second sub discharge port 512C can start communicating with the second inner compression chamber C22.

Further, the first sub discharge port 512b and the second sub discharge port 512C may be simultaneously shielded from the second outer compression chamber C21 and the second inner compression chamber C22. That is, when the communication between the first sub discharge port 512b and the second outer compression chamber C21 is completed, the communication between the second sub discharge port 512C and the second inner compression chamber C22 may be completed.

On the other hand, in the discharge valve 600, the main opening/closing part 610, the first sub opening/closing part 630, the second sub opening/closing part 650, the fastening part 670, the main supporting part 620, the first sub supporting part 640, and the second sub supporting part 660 may be integrally formed to minimize increase in cost and weight of the discharge valve 600, and the fastening part 670 may have a circumferential width smaller than a distance between the first sub opening/closing part 630 and the second sub opening/closing part 650 and may be fastened to the fixed hard plate 510 by one fastening member 680. Here, it is preferable that even if the discharge valve 600 is fastened to the fixed hard plate 510 by the one fastening member 680, the one fastening member 680 should be fastened to a side of a fixed scroll inlet portion 532, which will be described later, having a relatively large thickness and height, so as to receive a sufficient supporting force.

As described above, since the discharge valve 600 is integrally formed and the fastening portion 670 has a narrow width and is fastened to the fixed hard plate 510 by the one fastening member 680, at least one of the first and second sub-supporting portions 640 and 660 may interfere with the inlet 514 due to a low degree of freedom in design, and in order to prevent this, at least one of the first and second sub-supporting portions 640 and 660 may include a recess 690 that is recessed toward the main supporting portion 620.

The inlet 514 may be formed in a long hole to increase the flow rate of the refrigerant injected into the compression chamber C.

The cross-sectional shape of the inlet 514 may be constant to prevent pressure loss and flow loss from occurring during the refrigerant passing through the inlet 514. That is, the inner diameter of the inlet 514 may be a predetermined value regardless of the axial position of the inlet 514.

The injection port 514 may be formed in plurality so as to supply the refrigerant discharged from the injection valve assembly 700 to each of the pair of first compression chambers C1. That is, the injection port 514 may include: a first inlet 514a which communicates with the first outer compression chamber C11; and a second inlet port 514b communicating with the first inner compression chamber C12, wherein the first inlet port 514a and the second inlet port 514b are formed on opposite sides with respect to a virtual line connecting the first sub-discharge port 512b and the second sub-discharge port 512C.

The inlet 514 may be connected to both the first outer compression chamber C11 and the first inner compression chamber C12, so as to prevent pressure from being non-uniform between the first outer compression chamber C11 and the first inner compression chamber C12. That is, as shown in fig. 16 to 20, when the first inlet 514a communicates with the first outer compression chamber C11, the second inlet 514b communicates with the first inner compression chamber C12.

Further, the inlet 514 may be preferably shielded from the first outer compression chamber C11 and the first inner compression chamber C12 at the same time. That is, as shown in fig. 16 to 20, when the communication between the first inlet 514a and the first outer compression chamber C11 is completed, the communication between the second inlet 514b and the first inner compression chamber C12 may be completed.

On the other hand, the fixed hard plate 510 may further include a small diameter portion insertion groove 516 for preventing leakage of the refrigerant when the refrigerant flows from the injection valve assembly 700 toward the first and second injection ports 514a and 514 b. That is, the fixing hard sheet 510 may further include: a first small-diameter portion insertion groove 516a into which a first small-diameter portion 732ab described later is inserted; and a second small-diameter portion insertion groove 516b into which a second small-diameter portion 732bb described later is inserted.

Specifically, the fixing hard plate 510 may include: a fixed hard plate upper surface 510a facing the injection valve assembly 700; and a fixed hard plate lower surface 510b forming a rear surface of the fixed hard plate upper surface 510a and facing the orbiting scroll 400.

The first small diameter portion insertion groove 516a may be formed by engraving from the fixed hard board upper surface 510a toward the fixed hard board lower surface 510b, and a first small diameter portion 732ab described later may be inserted therein, and the first inlet 514a may be formed by engraving from the fixed hard board lower surface 510b toward the fixed hard board upper surface 510a, and may communicate with the first small diameter portion insertion groove 516 a.

The second small diameter portion insertion groove 516b may be formed by engraving from the fixed hard board upper surface 510a toward the fixed hard board lower surface 510b, and a second small diameter portion 732bb described later may be inserted, and the second inlet 514b may be formed by engraving from the fixed hard board lower surface 510b toward the fixed hard board upper surface 510a, and may communicate with the second small diameter portion insertion groove 516 b.

As shown in fig. 4, a first small diameter portion 732ab, which will be described later, may be inserted into the first small diameter portion insertion groove 516a, an inner diameter of the first small diameter portion 732ab, which will be described later, (an inner diameter of the first outlet port 736a, which will be described later) may be greater than or equal to an inner diameter of the first main inlet port 514a, and an inner diameter of the first small diameter portion insertion groove 516a may be the same as an outer diameter of the first small diameter portion 732ab, which will be described later, in order to prevent pressure loss and flow loss from occurring during the flow of the refrigerant from the injection valve assembly 700 to the first injection port 514 a. That is, since the first small diameter portion 732ab described later has an outer diameter larger than the inner diameter of the first small neck portion 732ab described later, the inner diameter of the first small diameter portion insertion groove 516a may be larger than the inner diameter of the first inlet 514 a.

A second small diameter portion 732bb, which will be described later, may be inserted into the second small diameter portion insertion groove 516b, an inner diameter of the second small diameter portion 732bb, which will be described later (an inner diameter of the second outlet 736b, which will be described later), may be equal to or larger than an inner diameter of the second inlet 514b, and an inner diameter of the second small diameter portion insertion groove 516b may be equal to an outer diameter of the second small diameter portion 732bb, which will be described later, in order to prevent pressure loss and flow loss from occurring during the flow of the refrigerant from the inlet valve assembly 700 to the second inlet 514 b. That is, since the second small-diameter portion 732bb, which will be described later, has an outer diameter larger than the inner diameter of the second small-diameter portion 732bb, which will be described later, the inner diameter of the second small-diameter portion insertion groove 516b may be larger than the inner diameter of the second inlet 514 b.

The fixed wrap 520 may be formed to extend from a central side position of the fixed scroll 500 toward an outer circumferential side of the fixed scroll 500, and may be formed to extend in a logarithmic spiral shape, for example.

The fixed side plate 530 may have a ring shape extending along an outer circumferential portion of the fixed hard plate 510, and may include a fixed scroll inlet portion 532 connected to the fixed scroll 520 at one side.

The fixed scroll inlet 532 may have the same axial height as that of the fixed scroll 520, so as to prevent the refrigerant of the compression chamber C from leaking through the fixed scroll inlet 532.

Also, the radial thickness of the orbiting scroll inlet portion 532 may be greater than the radial thickness of the fixed scroll 520 to improve the support rigidity of the fixed scroll 520.

In order to reduce the weight and cost of the fixed scroll 500, the fixed side plate 530 may have a radial thickness smaller than that of the fixed scroll inlet 532 except for the fixed scroll inlet 532.

The injection valve assembly 700 may be formed at a front end surface of the third annular wall 138 to communicate with and block the introduction chamber I and the injection port 514.

Specifically, as shown in fig. 2 to 4 and 8 to 12, the injection valve assembly 700 may include: a cover plate 710 connected to a front end surface of the third annular wall 138 to cover the introduction chamber I; a valve plate 730 fastened to the cover plate 710 on the opposite side of the introduction chamber I with respect to the cover plate 710; and an injection valve 720 formed between the cap plate 710 and the valve plate 730.

The cover plate 710 may include: a cover plate upper surface 710a facing the introduction chamber I and the third annular wall 138; a cover lower surface 710b facing the valve plate 730 and the injection valve 720; and an injection valve insertion groove 710c formed by engraving from the cover plate lower surface 710b at the center of the cover plate 710.

Moreover, the cover plate 710 may further include: an inlet 712 for communicating the introduction chamber I with an inclined space 734 described later; a second fastening hole 714 communicating with the fastening groove 138a and penetrating through the fastening bolt 770; and a first positioning hole 716 communicating with the first positioning groove 138b and penetrating through the positioning pin 780.

The inflow port 712 may be formed at a center portion of the cover plate 710, and may penetrate the cover plate 710 from the cover plate upper surface 710a to the injection valve seating groove 710 c.

The second fastening hole 714 may be formed in an outer circumferential portion of the cover plate 710, and may penetrate the cover plate 710 from the cover plate upper surface 710a to the cover plate lower surface 710 b.

The first positioning hole 716 may be formed between the inflow port 712 and the second fastening hole 714 in the radial direction of the cover plate 710, and may penetrate the cover plate 710 from the cover plate upper surface 710a to the injection valve seating groove 710 c.

The injection valve 720 may include: a head 722 for opening or closing the inflow port 712; a leg 724 for supporting the head 722; and a peripheral portion 726 for supporting the leg portion 724.

The head 722 may be formed in a disc shape having an outer diameter larger than an inner diameter of the inflow port 712.

The leg portion 724 may be formed in a plate shape and extend in one direction from the head portion 722 to the peripheral portion 726.

The peripheral portion 726 may be formed in a ring shape, and may be received in the injection valve insertion groove 710c and may receive the head portion 722 and the leg portion 724.

The peripheral portion 726 may include a second positioning hole 726a communicating with the first positioning hole 716 and penetrating through the positioning pin 780.

In the injection valve 720, the axial thickness of the peripheral portion 726 may be greater than or equal to the axial depth of the injection valve seating groove 710c (more precisely, the distance between the basal surface of the injection valve seating groove 710c and a valve plate upper surface 730a described later), so that the peripheral portion 726 is pressed and fixed between the injection valve seating groove 710c and the valve plate 730 without an additional fastening portion for fixing the injection valve 720. In this case, in order to prevent the peripheral portion 726 from being not pressed against the valve plate 730 by the tolerance between the injection valve seating groove 710c, the axial thickness of the peripheral portion 726 should preferably be larger than the axial depth of the injection valve seating groove 710 c.

The valve plate 730 may include: a valve plate upper surface 730a facing the cover plate 710 and the injection valve 720; and a valve plate lower surface 730b forming a rear surface of the valve plate upper surface 730a and facing the fixed scroll 500.

The valve plate 730 may further include a protrusion 732 protruding from the lower surface 730b of the valve plate toward the first and second inlet ports 514a and 514 b. That is, the valve plate 730 may include: a first protrusion 732a protruding from one side of the valve plate lower surface 730b toward the first inlet port 514 a; and a second protrusion 732b protruding from the other side of the valve plate lower surface 730b toward the second inlet port 514 b.

Moreover, the valve plate 730 may further include: an inclined space 734 functioning as a retainer of the injection valve 720 and receiving the refrigerant flowing in through the inlet 712; a first outlet 736a formed in the first protrusion 732a and communicating with the first inlet 514 a; a second outlet 736b formed in the second projection 732b and communicating with the second inlet 514 b; a first connection passage 738a for guiding the refrigerant in the inclined space 734 to the first outlet 736 a; and a second connection passage 738b for guiding the refrigerant in the inclined space 734 to the second outlet 736 b.

The valve plate upper surface 730a may be formed as a flat surface contacting the cover plate lower surface 710b and the peripheral portion 726 of the injection valve 720.

The inclined space 734 may be engraved from the valve plate upper surface 730 a.

Also, the inclined space 734 may include a fixing surface for supporting the head 722 and the leg 724 of the injection valve 720 when the injection valve 720 opens the inflow port 712.

The first outlet 736a may be engraved from a distal end surface of the first projecting portion 732a (more precisely, a distal end surface of a first small diameter portion 732ab, which will be described later).

The second outlet 736b may be engraved from a distal end surface of the second protrusion 732b (more precisely, a distal end surface of a second small diameter portion 732bb described later).

The first connection passage 738a may be engraved from the valve plate upper surface 730a to communicate one side of the inclined space 734 with the first outlet port 736 a.

The second connection passage 738b may be engraved from the valve plate upper surface 730a to communicate the other side of the inclined space 734 with the second outlet 736 b.

The valve plate lower surface 730b may be spaced apart from the fixed hard plate upper surface 510a such that the discharge valve 600 is formed between the fixed hard plate upper surface 510a and the valve plate lower surface 730b and such that the refrigerant discharged from the discharge port 512 can flow toward the discharge chamber D.

The first protrusion 732a may include: a first large diameter portion 732aa protruding from one side of the valve plate lower surface 730b toward the first inlet port 514 a; and a first small diameter part 732ab protruding further toward the first inlet 514a from the first large diameter part 732 aa.

The outer diameter of the first large diameter part 732aa may be larger than the inner diameter of the first small diameter part insertion groove 516a so that the first large diameter part 732aa is prevented from being inserted into the first small neck part insertion groove 516a, and a third seal member 760 described later may be pressed between the distal end surface of the first large diameter part 732aa and the fixed hard plate upper surface 510 a.

The first small diameter part 732ab may have an outer diameter smaller than that of the first large diameter part 732aa and the same inner diameter as that of the first small neck insertion groove 516a, so that the first small diameter part 732ab may be inserted into the first small diameter part insertion groove 516 a.

The length of projection of the first small diameter portion 732ab (the length in the axial direction between the distal end surface of the first large diameter portion 732aa and the distal end surface of the first small diameter portion 732 ab) may be greater than the thickness of the third seal member 760 before deformation described below and equal to or less than the sum of the thickness of the third seal member 760 before deformation described below and the axial depth of the first small diameter portion insertion groove 516a described below, so as to prevent the front end surface of the first small-diameter portion 732ab from contacting the basal surface of the first small-diameter portion insertion groove 516a, the distance between the distal end surface of the first large diameter portion 732aa and the fixed hard plate upper surface 510a is set to be equal to or smaller than the thickness of the third seal member 760 before deformation (the thickness before pressure contact between the fixed hard plate upper surface 510a and the distal end surface of the first large diameter portion 732 aa), so that a third seal member 760 described later can be pressed between the front end surface of the first large diameter portion 732aa and the fixed hard plate upper surface 510 a. However, in order to cope with the case where the third seal member 760 described later cannot be pressed between the front end surface of the first large diameter portion 732aa and the fixed hard plate upper surface 510a due to tolerance, the protruding length of the first small diameter portion 732ab is preferably designed to be larger than the thickness of the third seal member 760 described later before deformation and smaller than the sum of the thickness of the third seal member 760 described later before deformation and the axial depth of the first small diameter portion insertion groove 516a described later.

The second protrusion 732a may be similar to the first protrusion 732 a.

That is, the second protrusion 732b may include: a second large diameter portion 732ba protruding from the other side of the valve plate lower surface 730b toward the second inlet port 514 b; and a second small diameter portion 732bb protruding from the second large diameter portion 732ba toward the second inlet 514 b.

The second large diameter portion 732ba may have an outer diameter larger than an inner diameter of the second small diameter portion insertion groove 516b so as to prevent the second large diameter portion 732ba from being inserted into the second small diameter portion insertion groove 516b, and a third seal member 760 to be described later may be pressed between a distal end surface of the second large diameter portion 732ba and the fixed hard plate upper surface 510 a.

The second small diameter portion 732bb may have an outer diameter smaller than the outer diameter of the second large diameter portion 732ba or the same as the inner diameter of the second small diameter portion insertion groove 516b, so that the second small diameter portion 732bb may be inserted into the second small diameter portion insertion groove 516 b.

The length of projection of the second small diameter portion 732bb (the axial length between the distal end surface of the second large diameter portion 732ba and the distal end surface of the second small diameter portion 732 bb) may be greater than the thickness of the third seal member 760 before deformation described below and less than or equal to the sum of the thickness of the third seal member 760 before deformation described below and the axial depth of the second small diameter portion insertion groove 516b described above, so as to prevent the front end surface of the second small diameter portion 732bb from contacting the basal surface of the second small diameter portion insertion groove 516b, the distance between the distal end surface of the second large diameter portion 732ba and the fixed hard plate upper surface 510a is set to be equal to or smaller than the thickness of the third seal member 760 before deformation (the thickness before being pressed between the fixed hard plate upper surface 510a and the distal end surface of the second large diameter portion 732 ba), so that a third seal member 760 described later can be pressed between the front end surface of the second large diameter portion 732ba and the fixed hard plate upper surface 510 a. However, in order to cope with the case where the third seal member 760 described later cannot be pressed between the distal end surface of the second large diameter portion 732ba and the fixed hard plate upper surface 510a due to tolerance, the protruding length of the second small diameter portion 732bb is preferably designed to be larger than the thickness of the third seal member 760 described later before deformation and smaller than the sum of the thickness of the third seal member 760 described later before deformation and the axial depth of the second small diameter portion insertion groove 516b described later.

The valve plate 730 may further include a first fastening hole 739a, and the first fastening hole 739a may be formed at an outer circumferential portion of the valve plate 730 to penetrate the valve plate 730 from the valve plate upper surface 730a to the valve plate lower surface 730b, to communicate with the second fastening hole 714, and to penetrate the second fastening hole 714 by the fastening bolt 770.

Also, the valve plate 730 may further include a second positioning groove 739b engraved from the upper surface 730a thereof to communicate with the second positioning hole 726a so as to insert the positioning pin 780.

The injection valve assembly 700 is fastened to the rear case 130 by the fastening bolt 770, the first fastening hole 739a, the second fastening hole 714, and the fastening groove 138a after being aligned by the positioning pin 780, the first positioning hole 716, the second positioning hole 726a, the first positioning groove 138b, and the second positioning groove 739 b. That is, one end of the positioning pin 780 may be inserted into the first positioning groove 138b through the first positioning hole 716, and the other end of the positioning pin 780 may be inserted into the second positioning groove 739b through the second positioning hole 726a, whereby the cover plate 710, the injection valve 720, and the valve plate 730 may be disposed at predetermined positions. The fastening bolt 770 may be fastened to the fastening groove 138a by penetrating the first fastening hole 739a and the second fastening hole 714, so that the injection valve assembly 700 may be fastened to the rear case 130.

On the other hand, as shown in fig. 2 to 4 and 8, when the injection valve assembly 700 is fastened to the rear housing 130, a first sealing member 740 may be formed between the cover plate upper surface 710a and the third annular wall 138, and a second sealing member 750 may be formed between the valve plate upper surface 730a and the cover plate lower surface 710 b.

As shown in fig. 2 to 4 and 12, when the injection valve assembly 700 is fastened to the fixed scroll 500, a third seal member 760 may be formed between the distal end surfaces of the large diameter portions 732aa and 732ba and the fixed hard plate upper surface 510 a.

As described above, the thickness of the third seal member 760 before deformation may be greater than or equal to the distance between the tip end portions of the large diameter portions 732aa and 732ba and the fixed hard plate upper surface 510a, so that the third seal member 760 may be pressed between the tip end surfaces of the large diameter portions 732aa and 732ba and the fixed hard plate upper surface 510 a.

On the other hand, unexplained reference numerals 718 and 719 are a first groove 718 and a second groove 719 formed in the cover plate 710, and unexplained reference numerals 518 and 519 are a third groove 518 and a fourth groove 519 formed in the fixing hard plate 510.

The first groove 718 may have a ring shape formed by being engraved from the injection valve seating groove 710c and surrounding the periphery of the inflow port 712, as shown in fig. 10, in order to reduce noise generated by collision between the head 722 of the injection valve 720 and the cover plate 710 by reducing a contact area between the head 722 of the injection valve 720 and the cover plate 710, and prevent foreign substances from being caught between the head 722 of the injection valve 720 and the cover plate 710 by trapping and discharging the foreign substances. Further, an inner circumferential portion of the first groove 718 and an outer circumferential portion of the head portion 722 of the injection valve 720 may overlap in the axial direction, and the outer circumferential portion of the first groove 718 does not overlap in the axial direction with the head portion 722 of the injection valve 720. That is, the inner diameter of the first groove 718 may be smaller than the outer diameter of the head 722 of the injection valve 720, and the outer diameter of the first groove 718 may be larger than the outer diameter of the head 722 of the injection valve 720. The outer diameter of the first groove 718 is larger than the outer diameter of the head 722 of the injection valve 720 so that the foreign matters trapped in the first groove 718 are discharged toward the inclined space 734.

The second groove 719 may prevent foreign substances from being caught between the leg 724 of the injection valve 720 and the cover 710 by trapping and discharging the foreign substances, and as shown in fig. 10, the second groove 719 may be engraved from the injection valve seating groove 710c at a position facing the leg 724 of the injection valve 720. The second groove 719 may have a long hole shape, a central portion of the second groove 719 may axially overlap the leg portion 724 of the injection valve 720, and both end portions of the second groove 719 may not axially overlap the leg portion 724 of the injection valve 720. That is, the long axis direction of the second groove 719 may be parallel to the width direction of the leg 724 of the injection valve 720, and the long axis length of the second groove 719 may be greater than the width of the leg 724 of the injection valve 720. The length of the second groove 719 along the long axis thereof should be greater than the width of the leg 724 of the injection valve 720 so that foreign matter trapped in the second groove 719 can be discharged toward the inclined space 734.

The third groove 518 may have a ring shape engraved from the upper surface 510a of the fixed hard plate to surround the periphery of the main discharge port 512a, as shown in fig. 8 and 13, in which noise generated by collision between the main opening/closing portion 610 of the discharge valve 600 and the fixed hard plate 510 is reduced by reducing a contact area between the main opening/closing portion 610 of the discharge valve 600 and the fixed hard plate 510, and foreign substances are prevented from being caught and discharged between the main opening/closing portion 610 of the discharge valve 600 and the fixed hard plate 510, similarly to the first groove 718. Further, an inner peripheral portion of the third groove 518 may axially overlap with an outer peripheral portion of the opening/closing portion of the discharge valve 600, and the outer peripheral portion of the third groove 518 may not axially overlap with the opening/closing portion of the discharge valve 600. That is, the inner diameter of the third groove 518 may be smaller than the outer diameter of the opening/closing portion of the discharge valve 600, and the outer diameter of the third groove 518 may be larger than the outer diameter of the opening/closing portion of the discharge valve 600. The third groove 518 should have an outer diameter larger than that of the opening/closing portion of the discharge valve 600 so as to discharge the foreign matters trapped in the third groove 518 toward the discharge chamber D.

The fourth groove 519 is similar to the second groove 719 in that foreign substances are trapped and discharged to prevent the foreign substances from being caught between the main support part 620, the first sub-support part 640, and the second sub-support part 660 (hereinafter, referred to as "support parts") of the discharge valve 600 and the fixed hard plate 510, and the fourth groove 519 may be engraved from the upper surface 510a of the fixed hard plate at a position facing the support parts of the discharge valve 600 as shown in fig. 8 and 13. The fourth groove 519 may be formed in an elongated hole shape, a central portion of the fourth groove 519 may axially overlap with the support portion of the discharge valve 600, and both end portions of the fourth groove 519 may not axially overlap with the support portion of the discharge valve 600. That is, the longitudinal direction of the fourth groove 519 may be parallel to the width direction of the support portion of the discharge valve 600, and the longitudinal length of the fourth groove 519 may be greater than the width of the support portion of the discharge valve 600. The length of the long axis of the fourth groove 519 should be greater than the width of the support portion of the discharge valve 600 so that the foreign matter trapped in the fourth groove 519 can be discharged toward the discharge chamber D.

Hereinafter, the operation and effect of the scroll compressor of the present embodiment will be described

That is, when power is applied to the motor 200, the rotary shaft 300 may rotate together with the rotor 220.

The orbiting scroll 400 may be rotated by receiving a rotational force from the rotating shaft 300 through the eccentric bushing 310.

Thereby, the volume of the compression chamber C can be gradually reduced as the movement toward the center side is continued.

The refrigerant at the suction pressure can flow into the compression chamber C through the suction port (not shown), the motor accommodating space S1, the suction flow path (not shown), and the scroll accommodating space S2.

The refrigerant sucked into the compression chamber C may move to the center side along the moving path of the compression chamber C and be compressed, and may be discharged toward the discharge chamber D through the discharge port 512.

The refrigerant at the discharge pressure discharged into the discharge chamber D is discharged to the outside of the compressor through the discharge port 131.

However, the scroll compressor of the present embodiment may include an injection flow path (the introduction port 133, the introduction chamber I, the injection valve assembly 700, and the injection port 514) for introducing the refrigerant of the intermediate pressure into the compression chamber C, and the scroll compressor of the present embodiment may compress and discharge not only the refrigerant of the suction pressure but also the refrigerant of the intermediate pressure, and thus may increase the refrigerant discharge amount as compared to the case of sucking and compressing only the refrigerant of the suction pressure and discharging. This improves the performance and efficiency of the compressor.

Further, the rear case 130 may include the discharge chamber D, the discharge port 131, the introduction port 133, and the introduction chamber I without an additional case, that is, the rear case 130 having the discharge chamber D, the discharge port 131, the introduction port 133, and the introduction chamber I may be integrally formed, and thus, a possibility of leakage may be reduced and a size, a cost, and a weight may be reduced.

Further, as at least a part of the introduction chamber I is accommodated in the discharge chamber D, that is, a side portion of the introduction chamber I overlaps the discharge chamber D with the third annular wall 138 interposed therebetween, a distal end portion of the introduction chamber I overlaps the discharge chamber D with the injection valve assembly 700 interposed therebetween, and the refrigerant introduced to the injection port 514 can exchange heat with the refrigerant in the discharge chamber D through the third annular wall 138 and the injection valve assembly 700. That is, the refrigerant introduced into the chamber I and the refrigerant passing through the injection valve assembly 700 receive heat from the refrigerant in the discharge chamber D and are heated. This prevents the liquid refrigerant from being injected into the compression chamber C through the injection port 514.

As at least a portion of the discharge port 131 is accommodated in the introduction chamber I, that is, as at least a portion of the discharge port 131 overlaps the introduction chamber I with the wall portion of the discharge port 131 interposed therebetween, the refrigerant in the introduction chamber I can exchange heat with the refrigerant at the discharge port 131 through the wall portion of the discharge port 131 accommodated in the introduction chamber I. That is, the refrigerant introduced into the chamber I can receive heat from the refrigerant at the discharge port 131 and be heated. This can further prevent the liquid refrigerant from being injected into the compression chamber C through the injection port 514.

Further, as at least a part of the introduction port 133 is accommodated in the discharge chamber D, that is, as at least a part of the introduction port 133 overlaps the discharge chamber D with the wall of the introduction port 133 interposed therebetween, the refrigerant of the introduction port 133 can exchange heat with the refrigerant in the discharge chamber D through the wall of the introduction port 133 accommodated in the discharge chamber D. That is, the refrigerant in the inlet 133 can receive heat from the refrigerant in the discharge chamber D and be heated. This can further prevent the liquid refrigerant from being injected into the compression chamber C through the injection port 514.

As the refrigerant at the discharge port 131 and the refrigerant at the introduction port 133 flow in directions crossing each other, that is, as an angle between an outlet of the discharge port 131 and an inlet of the introduction port 133 is 0 degree or more and less than 90 degrees with respect to the center of the rear housing 130, the refrigerant at the introduction port 133 can exchange heat with the refrigerant at the discharge port 131. That is, the refrigerant in the inlet 133 can receive heat from the refrigerant in the outlet 131 and be heated. This can further effectively prevent the liquid refrigerant from being injected into the compression chamber C through the injection port 514.

The injection valve assembly 700 may include the cover plate 710, the injection valve 720, and the valve plate 730 may not only form a part of the injection flow path, but also perform a function of holding the injection valve 720, that is, the number of parts, size, cost, and weight of the injection valve assembly 700 may be reduced as the valve plate 730 includes the inclined space 734.

Further, as the injection valve 720 is formed so as to be pressed and fixed between the cover plate 710 (more precisely, the injection valve insertion groove 710c) and the valve plate 730 by the peripheral portion 726 of the injection valve 720, a fastening member for fastening the injection valve 720 to at least one of the cover plate 710 and the valve plate 730 can be omitted. This can further reduce the number of parts, size, cost, and weight of the injection valve assembly 700.

Also, after the injection valve assembly 700 is previously aligned by the positioning pins 780, it can be fastened to the rear case 130 at one time by the fastening bolts 770, so that the assembling property and the assembling quality can be improved.

Further, as the inlet port 514 simultaneously communicates with the pair of compression chambers C, that is, when the first inlet port 514a and the first outer compression chamber C11 start communicating with each other, the second inlet port 514b and the first inner compression chamber C12 start communicating with each other, so that it is possible to suppress pressure unevenness between the first outer compression chamber C11 and the first inner compression chamber C12 and to suppress abnormal behavior (for example, toppling over) of the orbiting scroll 400.

Additionally, since the communication between the second inlet port 514a and the first inner compression chamber C12 is terminated when the communication between the first inlet port 514a and the first outer compression chamber C11 is terminated, the abnormal behavior (for example, the turning over) of the orbiting scroll 400 can be further suppressed by further suppressing the pressure unevenness between the first outer compression chamber C11 and the first inner compression chamber C12.

However, the timing at which the injection port 514 simultaneously communicates with the pair of compression chambers C and the timing at which the injection port 514 simultaneously shields the pair of compression chambers C may be appropriately adjusted in consideration of the performance, efficiency, and the like of the scroll compressor.

On the other hand, in the present embodiment, the injection valve assembly 700 may branch the refrigerant flowing from the introduction chamber I in the inclined space 734 and guide the refrigerant to the first and second injection ports 514a and 514 b. That is, the inflow port 712, the head 722 of the injection valve 720, the leg 724 of the injection valve 720, and the inclined space 734 are formed in one piece, and the connection passage 738 and the outflow port 736 are formed in two pieces.

However, in this embodiment, the flow rates of the refrigerants distributed to the first inlet 514a and the second inlet 514b may be different from each other. In particular, when the first connection passage 738a and the first outlet port 736a are asymmetrical to the second connection passage 738b and the second outlet port 736b, the flow rates of the refrigerants distributed to the first inlet port 514a and the second inlet port 514b are more non-uniform due to the difference in flow resistance.

Therefore, as shown in fig. 21 to 24, the injection valve assembly 700 may guide the refrigerant flowing in from one side of the introduction chamber I to the first injection port 514a, and may guide the refrigerant flowing in from the other side of the introduction chamber I to the second injection port 514 b.

Specifically, the inflow port 712 may include: a first inlet 712a communicating with one side of the introduction chamber I; and a second inlet 712b formed separately from the first inlet 712a and communicating with the other side of the introduction chamber I.

Preferably, the first inlet 712a and the second inlet 712b may have a long hole shape to maximize a valve lifting force (valve lifting force) and an inflow rate of the refrigerant.

Also, the injection valve 720 may include: a first head 722a for opening or closing the first inlet 712 a; a first leg 724a for supporting the first head 722 a; a second head 722b for opening or closing the second inlet 712 b; a second leg 724b for supporting the second head 722 b; and a peripheral portion 726 for supporting the first leg portion 724a and the second leg portion 724 b.

Preferably, the first head 722a, the first leg 724a, the second head 722b, the second leg 724b, and the peripheral part 726 may be integrally formed to reduce the number of components, size, cost, and weight.

Further, it is more preferable that the first leg 724a and the second leg 724b are parallel to each other, and a connection portion between the first leg 724a and the peripheral portion 726 and a connection portion between the second leg 724b and the peripheral portion 726 are formed on opposite sides, so that it is more preferable in terms of compactness. That is, more preferably, the first leg 724a and the second leg 724b may be formed to be offset from each other.

Also, the inclined space 734 may include: a first inclined space 734a for receiving the refrigerant flowing in through the first inlet 712a, which has a function of fixing the first header 722 a; and a second inclined space 734b for receiving the refrigerant flowing in through the second inlet 712b, which has a function of fixing the second head 722 b.

Preferably, the first inclined space 734a and the second inclined space 734b are separable from each other, and a fixing surface of the first inclined space 734a and a fixing surface of the second inclined space 734b are inclined in a direction shifted so as to correspond to the first leg 724a and the second leg 724 b.

Also, the outflow port 736 includes: a first outlet 736a communicating with the first inlet 514 a; and a second outlet 736b communicating with the second inlet 514b, and the connection passage 738 may include: a first connection passage 738a which connects the first inclined space 734a and the first outlet 736 a; and a second connection passage 738b communicating the second inclined space 734b with the second outlet 736 b.

In the connection passage 738 and the outlet port 736, the first connection passage 738a may have an inner diameter larger than that of the first outlet port 736a and the second connection passage 738b may have an inner diameter larger than that of the second outlet port 736b, so that pressure loss and flow loss are prevented from occurring while the refrigerant passes through the connection passage 738 and the outlet port 736.

As described above, in another embodiment of the present invention, as the refrigerant introduced into the inlet chamber I is separately introduced into the first inlet port 514a and the second inlet port 514b, the flow rates of the refrigerant distributed to the first inlet port 514a and the second inlet port 514b may be uniform.

On the other hand, in the above embodiment, the orbiting scroll 400 and the fixed scroll 500 may be accommodated in the rear housing 130, but is not limited thereto. That is, the fixed scroll 500 is formed between the rear housing 130 and the center housing 110 and exposed to the outside, and the orbiting scroll 400 may be accommodated in the fixed scroll 500.