CN1526951A - Compressor - Google Patents

Abstract

The present invention relates to a compressor, when refrigerant gas to be discharged to the outside of the compressor is discharged into a rear refrigerant gas discharge chamber and refrigerant gas to be discharged to the outside of the compressor is discharged to a front refrigerant gas discharge chamber , the compressor can reduce the pulsation pressure of the refrigerant gas in a multi-step manner, thereby achieving an excellent effect of reducing the pulsation pressure of the refrigerant gas and significantly reducing the pressure caused by the pulsation of the refrigerant gas. noise.

Description

compressor

technical field

The present invention relates to a compressor, especially a compressor capable of effectively reducing the pulsating pressure of refrigerant gas when discharging refrigerant gas.

Background technique

The compressor used in the air conditioning system of a motor vehicle can selectively receive the engine power transmitted by the pulley through the intermittent action of the electromagnetic clutch, and suck the refrigerant gas from the evaporator into it, and compress the refrigerant gas to compress the refrigerant gas The compressed refrigerant gas is discharged to the condenser. Compressors are divided into different types according to the compression structure, and the type widely used in motor vehicles is the swash plate compressor.

1 to 4 show the structure of a conventional swash plate compressor.

As shown in FIGS. 1 and 2, a general swash plate type compressor is constructed in such a manner that a swash plate 40 on which a drive shaft 30 is mounted is equipped with a pair of cylinders 10 and 20, respectively, and a plurality of pistons 50 in It is disposed on the outer surface of the swash plate 40 in such a manner as to be accommodated in a plurality of cylinder bores formed on the cylinder blocks 10 and 20 . As the swash plate 40 rotates, each piston 50 makes a linear reciprocating motion within the corresponding cylinder bore with the assistance of the piston shoe 60, whereby the piston absorbs and compresses the refrigerant gas. In this manner, the valve unit 70 provided with the suction valve 71, the valve plate 72, and the discharge valve 73 and the gasket are assembled outside the cylinder blocks 10 and 20 in the aforementioned order, respectively. In order to accommodate and protect the above components in the cylinder, the front housing 80 is connected to the cylinder 10 , and the rear housing 90 is connected to the cylinder 20 .

With the above-mentioned structure, when power is applied from the pulley of the electromagnetic clutch 31, this general swash plate type compressor rotates the swash plate 40, and whenever the swash plate 40 makes one revolution, it is provided outside the swash plate 40 The above-mentioned plurality of pistons 50 at the surface all start to reciprocate, thereby completing a stroke. Therefore, some of the above-mentioned plurality of pistons 50 move toward the front housing 80, while others move toward the rear housing 90 by means of the swash plate 40. The refrigerant gas of the casing 90 is delivered to the compression chambers 81 and 91, the plenum 96 of which has a suction muffler 94 and a discharge muffler 95, and the compression chambers 81 and 91 are formed by the front casing 80 and The inner side wall of the rear case 90 is formed. The refrigerant gas compressed in the compression chamber is delivered into the rear casing 90 through a predetermined passage, and mixed with the compressed refrigerant gas discharged from the rear casing 90, thereby being discharged to the outside of the compressor.

The passage structure and the operation of components for discharging compressed refrigerant gas to the outside will be described in more detail below. As shown in FIGS. 2 to 4 , a compression chamber 81 storing compressed refrigerant gas is formed at the central portion of the inner surface of the front housing 80 , and a pair of cylinders 10 and 20 are provided with guide holes 11 and 21 , the two guide holes 11 and 21 are provided at predetermined positions on the cylinder to correspond to each other, so that the guide hole can guide the refrigerant gas in the compression chamber 81 into the compression chamber 91 formed in the rear housing 90 . In the same way as the front case 80, the rear case 90 is provided with a compression chamber 91 and an exhaust passage 92, wherein the compression chamber 91 is arranged at the central portion of its inner surface, and in order to connect the exhaust chamber 93, the exhaust The passage 92 extends in the form of a curve along the peripheral wall surface of the compression chamber 91 for introducing the compressed refrigerant gas to the outside through the hole H. As shown in FIG.

Therefore, when the swash plate 40 rotates at a high speed, the above-mentioned plurality of pistons 50 reciprocates, thus compressing refrigerant gas in the compression chambers 81 and 91 of the front casing 80 and the rear casing 90, respectively. Then, through the guide holes 11 and 21 on the cylinder blocks 10 and 20, the refrigerant gas compressed in the compression chamber 81 of the front housing 80 is sent to the exhaust chamber 93 of the rear housing 90, and the refrigerant gas compressed in the rear housing 90 The refrigerant gas compressed in the compression chamber 91 of 90 is also delivered to the discharge chamber 93 through the discharge passage 92 . Thus, gases discharged from the compression chambers 81 and 91 of the front and rear casings are mixed in the discharge chamber 93 and discharged to the outside through the outlet port 94 .

However, in the general swash plate type compressor, since the exhaust passage 92 for discharging the refrigerant gas compressed in the rear housing 90 to the outside is usually formed separately in a semicircle on one side of the compression chamber 91, Therefore, an anti-leakage device such as a gasket must be used to close the upper opening on the other side of the compression chamber 91 . In addition, in order to seal the discharge passage, a separate part needs to be installed, which makes the structure of the compressor complicated.

In addition, the narrow and long semicircular structure of the exhaust passage 92 becomes an obstacle to the flow of refrigerant gas, eventually causing a pressure loss. The high-pressure refrigerant gas collides with the inner peripheral wall of the discharge passage 92, which causes undesirable noise generation due to pulsation of the refrigerant gas.

Since the exhaust passage 92 occupies a certain area of the suction chamber, which reduces the volume of the suction chamber, among the suction ports of the valve plate 72, the exhaust passage 92 partially covers the suction port provided thereon. 72a, therefore, operations that draw in refrigerant gas are often subject to significant resistance.

Also, the formation of the separate discharge passage 92 makes the structure of the compressor more complicated. In order to improve it, some modifications have been made with respect to the structure of the compression chamber 91 of the rear casing 90, and peripheral parts such as gaskets associated with the exhaust passage 92 have to be replaced. Contrary to what is required, this increases the number of process steps and leads to a considerable increase in production costs. In addition, since the suction and discharge of the refrigerant gas are not smooth, the discharge pressure of the refrigerant gas is reduced, and noise is generated due to the pulsation of the refrigerant gas.

To solve these problems, U.S. Patent No. 6,068,453 proposed by the assignee discloses a swash plate compressor, which is provided with exhaust passages arranged on the rear casing to improve the exhaust of refrigerant gas. air structure.

Fig. 5 is a front view of a compressor rear casing in the prior art.

As shown in the figure, the rear case 100 is provided with: a multi-sided inner wall 101 protruding upward from its inner bottom surface; The suction chamber 103 and the discharge chamber 104 are separated from each other by the walls, and a discharge pipe 106 is also provided to transport the compressed refrigerant gas discharged into the discharge chamber 104 to the outside of the compressor, One end of the exhaust pipe 106 extends a certain length in the exhaust chamber 104 , and the other end communicates with the outlet chamber 105 .

The exhaust pipe 106 of the rear housing 100 extends about half of the linear distance L between the point B on the inner surface of the inner wall 101 and the point A connecting the extension 102 with respect to its center line.

According to the structure in which the discharge pipe 106 is arranged inside the rear casing 100, the compressed refrigerant gas in the front casing and the compressed refrigerant gas in the rear casing are mixed in the outlet chamber 105 through the discharge pipe 106 to eliminate The two pulsating waves of refrigerant gas interact with each other and are then discharged outside the compressor.

However, in this prior art, when the refrigerant gas is discharged from the front casing to the outside of the compressor, since the pulsation pressure of the refrigerant gas cannot be effectively reduced, the decrease in the pulsation pressure of the refrigerant gas as a whole Little is restricted. Also, in order to solve this problem, a large exhaust muffler with a collector pipe is provided outside the compressor, which brings about another problem that the volume of the compressor must eventually increase.

Summary of the invention

Accordingly, the present invention is directed to a compressor that substantially solves one or more problems due to limitations and disadvantages of the related art.

An object of the present invention is to provide a compressor capable of effectively reducing the pulsating pressure of refrigerant gas when discharging the refrigerant gas.

Other advantages, purposes and characteristics of the present invention will be set forth in the following description, for those of ordinary skill in the art, after studying the following content, some advantages, purposes and characteristics will be obvious, or can also be obtained from implementing the present invention can be learned in practice. The objectives and other advantages of the invention may be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.

According to the present invention, there is provided a compressor comprising: a front casing closing one end of a front cylinder body; a rear casing closing one end of a rear cylinder body; a front cylinder arranged to be interconnected between the front casing and the rear casing Body and rear cylinder body; refrigerant gas inlet port and outlet port formed on at least one or more peripheral surfaces of the front cylinder body and rear cylinder body; The front discharge pipe, the above-mentioned first partition defines the front refrigerant gas discharge chamber to isolate it from the front refrigerant gas absorption chamber, thereby delivering the front refrigerant gas discharged into the front casing to the outside of the compressor Refrigerant gas in the discharge chamber; the front discharge pipe in the rear refrigerant gas absorption chamber passing through the second partition which defines the rear refrigerant gas discharge chamber so as to separate it from the rear refrigerant gas Isolation of the absorption chamber to deliver the refrigerant gas discharged into the rear refrigerant gas discharge chamber of the rear casing to the outside of the compressor; the front auxiliary expansion part communicated with the outlet side of the front discharge pipe and the rear discharge pipe and the rear auxiliary expansion part; the exhaust connection channel arranged in the front cylinder body and the rear cylinder body and connected with the front auxiliary expansion part and the rear auxiliary expansion part; and the exhaust connection channel communicates with the refrigerant gas outlet port according to The way to set the main expansion part.

According to the present invention, it is preferred that the main expansion part extends to one end of the exhaust connection channel of the front cylinder or the rear cylinder, forming an integral body in the front cylinder or the rear cylinder.

According to the present invention, it is preferable that the main expansion part is formed separately on the outer side of the front cylinder or the rear cylinder.

According to the present invention, it is preferable that at least one or more of the front exhaust pipe and the rear exhaust pipe are located at such positions that the front refrigerant gas discharge chamber and the rear refrigerant gas discharge chamber of the front casing and the rear casing The shortest distance between the gas discharge chamber and the center portion of the inlet ends of the front and rear exhaust pipes.

According to the present invention, it is preferable that at least one or more of the front auxiliary inflation portion and the rear auxiliary inflation portion have a larger volume than the front exhaust pipe and the rear exhaust pipe.

According to the present invention, it is preferred that at least one or more of the exhaust connecting passages have a cross-sectional area larger than or equal to those of the front exhaust pipe and the rear exhaust pipe.

According to the present invention, preferably, the volume of the main inflation part is larger than the sum of the volumes of the front auxiliary inflation part and the rear auxiliary inflation part or both are the same size.

According to the present invention, it is preferable that at least one or more of the front exhaust pipe and the rear exhaust pipe communicate with the lower surface of any one of the front auxiliary inflation portion and the rear auxiliary inflation portion.

According to the present invention, it is preferred that at least one or more passage cross-sectional areas of the front exhaust pipe and the rear exhaust pipe become larger or gradually increase from the inlet to the outlet.

According to the present invention, preferably, the passage length between the front exhaust pipe of the front casing and the refrigerant gas discharge end is equal to the passage length between the rear exhaust pipe of the rear casing and the refrigerant gas discharge end.

It is to be understood that both the foregoing general description and the following detailed description of the invention are exemplary and explanatory and are intended to provide further explanation of the invention as claimed.

Description of drawings

The accompanying drawings, which illustrate embodiments of the invention and together with the description serve to explain the principle of the invention, are incorporated in and constitute a part of this application to provide a further understanding of the invention. In these drawings:

Figure 1 is an exploded perspective view of a common compressor;

Figure 2 is a front sectional view of the compressor shown in Figure 1;

Fig. 3 is a front view of the front housing of the compressor shown in Fig. 1;

Fig. 4 is a front view of the rear casing of the compressor shown in Fig. 1;

Fig. 5 is a front view of a rear casing of a compressor in the prior art;

Fig. 6 is a side view of the compressor of the first embodiment of the present invention;

Fig. 7 is a side sectional view of the compressor shown in Fig. 6;

Fig. 8 is a front view of the front housing used in the compressor shown in Fig. 6;

Fig. 9 is a front view of the back casing employed in the compressor shown in Fig. 6; and

Fig. 10 is a side sectional view of a compressor according to a second embodiment of the present invention.

Detailed ways

Reference will now be made in detail to the preferred embodiments of the invention, examples of which are illustrated in the accompanying drawings.

Fig. 6 is a side view of the compressor according to the first embodiment of the present invention; Fig. 7 is a side sectional view of the compressor shown in Fig. 6; Fig. 8 is a front view of the front casing used in the compressor shown in Fig. 6; Fig. 9 is Figure 6 shows a front view of the back housing employed in the compressor.

In the first embodiment of the present invention, as shown in Figures 6 and 7, the compressor includes: a front casing 200 that closes one end of the front cylinder body 400; a rear casing 300 that closes one end of the rear cylinder body 500; The front cylinder block 400 and the rear cylinder block 500 combined with each other between the body 200 and the rear housing 300; the drive shaft 600 rotatably supported in the front cylinder block 400 and the rear cylinder block 500; a swash plate 700 ; and a plurality of pistons 900 operatively connected to the peripheral surface of the swash plate 700 through piston shoes 800 . For the sake of brevity, no description will be given below of structures similar or identical to those in conventional practice.

As shown in accompanying drawings 7 and 8, the rear portion of the front casing 200 is open, and the front refrigerant gas absorption chamber 210 and the front refrigerant gas absorption chamber 210 are set on the inner peripheral wall of the front casing (ie, on the inner surface of the front wall). Gas discharge chamber 220 . Wherein the front refrigerant gas absorption chamber 210 is used for supplying the refrigerant gas flowing into the compressor to the cylinder bore (not shown) on the front cylinder block 400 (see FIG. 7 ), and the front refrigerant gas discharge chamber 220 is used for The compressed refrigerant gas flowing out of the cylinder bore is discharged to the outside of the compressor. The front refrigerant gas absorption chamber 210 is isolated from the front refrigerant gas discharge chamber 220 by a partition 230 . The partition 230 is generally in the form of a closed curve and is located on the outer surface of the front refrigerant gas discharge chamber 220 . From the front of the front wall surface of the front housing 200 at the central portion of the front refrigerant gas discharge chamber 220, there is provided a pulley (not shown) rotatably mounted through a bearing (not shown), supporting the nose portion 202 of the drive shaft 600. (see FIG. 8 ) rotatably protrudes, and the drive shaft 600 passes through the nose.

In addition, as shown in FIGS. 7 and 9 , the rear housing 300 is opened at the front and equipped with a rear cylinder 500 . The rear casing 300 is provided with a rear refrigerant gas absorption chamber 310 and a rear refrigerant gas discharge chamber 320 on its inner peripheral wall (ie, on the inner surface of the rear wall), wherein the rear refrigerant gas absorption chamber 310 is used for The cylinder bore (not shown) on the rear cylinder block 500 (see FIG. 7 ) is supplied with the refrigerant gas flowing into the compressor, and the rear refrigerant gas discharge chamber 320 is used to discharge the compressed gas flowing out of the cylinder bore to the outside of the compressor. Refrigerant gas. The rear refrigerant gas absorption chamber 310 is isolated from the rear refrigerant gas discharge chamber 320 by a partition 330 . The shape of the partition 330 is generally in the form of a closed curve, and is located on the outer surface of the rear refrigerant gas discharge chamber 320 .

As shown in Figure 7, the front cylinder block 400 is provided with an exhaust connection passage 410, and the rear cylinder block 500 is provided with an exhaust connection passage 510, and the exhaust connection passages 410 and 510 communicate with each other, so that the front housing 200 and the rear housing The refrigerant gas discharged from 300 is discharged to the refrigerant gas outlet port 530 . The exhaust connection passage 410 is connected with the front auxiliary inflation part 250 of the front case 200 , and the exhaust connection passage 510 is connected with the rear auxiliary inflation part 350 of the rear case 300 . The exhaust connecting passages 410 and 510 are extended at their ends to form the main expansion part 420 as an integral piece in the front and rear cylinders.

In a preferred embodiment of the present invention, the refrigerant gas inlet port 520 and the refrigerant gas outlet port 530 are located on the peripheral surface of the rear cylinder 500 , but they may also be located on the peripheral surface of the front cylinder 400 . Also, if one of them is disposed on the peripheral surface of the front cylinder 400 , the other may be disposed on the peripheral surface of the rear cylinder 500 .

Referring to these passages below, as shown in FIG. 7 , the drive shaft 600 is driven to rotate by the power delivered from the power source, and the swash plate 700 also rotates thereupon. Like this, according to the phases (phases) of the swash plate 700, A plurality of pistons 900 reciprocate in the respective cylinder holes of the front cylinder 400 and the rear cylinder 500, and at this time, refrigerant gas is sucked, compressed and then discharged through the passages in the compressor employing the above structure. During the reciprocating motion of the plurality of pistons 900, a negative pressure is formed in the bore of the cylinder, so that the refrigerant gas flows into the swash plate chamber S through the refrigerant gas inlet port 520 connected to the evaporator (not shown).

The refrigerant gas introduced into the swash plate chamber S is sucked into the cylinder bores of the front block 400 and the rear block 500, respectively.

When the refrigerant gas sucked into the cylinder bore is compressed by the compression stroke of the piston 900, the gas flows to the front of the front housing 200 and the rear housing 300 through the opening formed in the valve plate and the opening on the suction needle valve. The refrigerant gas discharge chamber 220 and the rear refrigerant gas discharge chamber 320 are discharged, and openings formed in the above valve plates are opened by a discharge needle valve.

Refer to the passage through which the refrigerant gas flowing into the front refrigerant gas discharge chamber 220 and the rear refrigerant gas discharge chamber 320 of the front housing 200 and the rear housing 300 is discharged to the outside of the compressor, respectively from the front The refrigerant gas discharged from the casing 200 and the rear casing 300 is transported to the refrigerant gas discharge port 530 by the exhaust connection passages 410 and 510 of the front cylinder block 400 and the rear cylinder block 500, and the refrigerant gas passes through the discharge port to the compressor. external emissions.

In this way, as shown in accompanying drawings 6 and 7, the front casing 200 and the rear casing 300 are provided with a front exhaust pipe 240 and a rear exhaust pipe 340, and the front exhaust pipe 240 and the rear exhaust pipe 340 are arranged from the front The refrigerant gas discharge chamber 220 and the rear refrigerant gas discharge chamber 320 extend through the partitions 230 and 330, and are provided with auxiliary expansion parts 250 and 250 at openings of the front exhaust pipe 240 and the rear exhaust pipe 340 350.

In this way, the refrigerant gas in the rear refrigerant gas discharge chamber 320 is delivered to the exhaust connection channel 510 of the rear cylinder block 500 through the rear discharge conduit 340 and the auxiliary expansion part 350 , and then passes through the front exhaust pipe 240 and the auxiliary expansion part. part 250, the refrigerant gas in the front refrigerant gas discharge chamber 220 is transported into the exhaust connection channel 410 of the front cylinder block 400, and then this part of the refrigerant gas is transported from the exhaust connection channel 510 of the rear cylinder body 500 The incoming refrigerant gas passes through the main expansion section 420 together. Thereafter, the refrigerant gas is discharged to the outside of the compressor through the refrigerant gas discharge port 530 .

The front exhaust pipe 240 and the rear exhaust pipe 340 discharge refrigerant gas from the front refrigerant gas discharge chamber 220 and the rear refrigerant gas discharge chamber 320 to the auxiliary expansion parts 250 and 350 , and the two exhaust pipes are connected with the separator 230 communicates with the upper surface of 330, in this case, when the refrigerant gas flows toward the exhaust connection passages 410 and 510, it may stay at the bottom of the auxiliary expansion parts 250 and 350, which makes it difficult to reduce the refrigerant gas pulsating pressure. In a preferred embodiment of the present invention, in order to prevent the refrigerant gas from staying in the auxiliary expansion part, at least one or more of the front exhaust pipe 240 and the rear exhaust pipe 340 of the front housing 200 and the rear housing 300 are connected with the auxiliary expansion part. The bottom surfaces of the portions 250 and 350 communicate.

In addition, in a preferred embodiment of the present invention, the length of the channel between the front exhaust pipe 240 of the front housing 200 and the refrigerant gas exhaust port 530 is the same as the length of the passage between the rear exhaust pipe 340 of the rear housing 300 and the refrigerant gas exhaust port. The passage lengths between the gas ports 530 are equal, and as a result, the difference between the pulsation pressures of the refrigerant gas discharged from the front case 200 and the rear case 300 is substantially the same as each other, thus reducing the pulsation pressure of the refrigerant gas.

In addition, in a preferred embodiment of the present invention, in order to effectively reduce the pulsating pressure generated when the refrigerant gas is discharged from the front casing 200 and the rear casing 300 to the outside of the compressor, it is preferable that the auxiliary expansion parts 250 and 350 The volume is larger than the volume of the front exhaust pipe 240 and the rear exhaust pipe 340. That is, the refrigerant gas delivered from the front refrigerant gas discharge chamber 220 and the rear refrigerant gas discharge chamber 320 flows into the large-volume auxiliary expansion part through the small-volume front exhaust pipe 240 and the rear exhaust pipe 340 250 and 350, which reduces the pulsating pressure of the refrigerant gas. In addition, in a preferred embodiment of the present invention, at least one or more of the front exhaust pipe 240 and the rear exhaust pipe 340 has a cross-sectional area of the passage that becomes larger or gradually increases from the inlet to the outlet. Large, at least one or more of the front exhaust pipe 240 and the rear exhaust pipe 340 are located at such positions that the front refrigerant gas discharge chamber 220 and the rear refrigerant gas discharge chamber 220 of the front casing 200 and the rear casing 300 The shortest distances L1 and L2 between the central portion of the chamber 320 and its inlet end.

In addition, if the passage cross-sectional area of the front exhaust pipe 240 and the rear exhaust pipe 340 is larger than that of the exhaust connection passages 410 and 510, the amount of refrigerant gas flowing into the front auxiliary expansion part 250 and the rear auxiliary expansion part 350 becomes smaller. greater than the amount of refrigerant gas flowing out therefrom so that the refrigerant gas stays in the front auxiliary expansion portion 250 and the rear auxiliary expansion portion 350 . Therefore, preferably, the cross-sectional areas of the exhaust connection passages 410 and 510 are larger than those of the front exhaust pipe 240 and the rear exhaust pipe 340 or are the same in size.

As discussed above, in particular, in order to prevent refrigerant gas from staying in the front auxiliary expansion part 250 and the rear auxiliary expansion part 350, the volume of the main expansion part 420 is greater than the sum of the volumes of the front auxiliary expansion part 250 and the rear auxiliary expansion part 350 or Both are equal in size.

Because the cross-sectional areas of the exhaust connecting passages 410, 510 and the main expansion part 420 are not equal to each other, the effect of noise reduction is achieved during the process of transporting the refrigerant gas to the exhaust connecting passages 410, 510 and the main expansion part 420, This greatly reduces the pulsating pressure of the refrigerant gas.

When the refrigerant gas to be discharged to the outside of the compressor is discharged into the rear refrigerant gas discharge chamber 320 and the refrigerant gas to be discharged to the outside of the compressor is discharged to the front refrigerant gas discharge chamber 220, the preferred embodiment of the present invention The embodiment adopts multiple steps to reduce the pulsating pressure of the refrigerant gas, thereby achieving an excellent effect of reducing the pulsating pressure of the refrigerant gas.

Fig. 10 is a side sectional view of a compressor according to a second embodiment of the present invention.

As shown in Figure 10, in the second embodiment of the present invention, the structure and action process of the compressor are the same as those of the first embodiment of the present invention except for the following difference: the main expansion part 420 is connected to the front cylinder The front exhaust connection passage 410 and the rear exhaust connection passage 510 in the body 400 and the rear cylinder block 500 are connected, and the main expansion part 420 is separately formed on the peripheral surface of the front cylinder block 400 or the rear cylinder block 500 .

In this way, because the pulsation pressure of the discharged refrigerant gas is reduced through the exhaust pipes 240, 340, the front auxiliary expansion part 250, and the rear auxiliary expansion part 350, it is different from the conventional plenum or exhaust muffler. Compared with that, the size of the main expansion part 420 is greatly reduced, therefore, this way can reduce the size of the overall assembly of the compressor.

Although the preferred embodiment of the present invention is applicable to a compressor structure in which the front housing 200 and the rear housing 300 are connected by the front housing 200 and the rear housing 300 to the ends of the front cylinder 400 and the rear cylinder 500 Closed in such a way that they are connected to each other, however, these preferred embodiments can also be applied in the same manner to a compressor mechanism in which the front cylinder block 400 and the rear cylinder block 500 are arranged and assembled in the front casing 200 and the rear casing body 300 interior.

As clearly explained above, when the refrigerant gas to be discharged to the outside of the compressor is discharged into the rear refrigerant gas discharge chamber, and the refrigerant gas to be discharged to the outside of the compressor is discharged to the front refrigerant gas discharge chamber chamber, the compressor of the preferred embodiment of the present invention can reduce the pulsating pressure of the refrigerant gas in a multi-step manner, thereby achieving an excellent effect of reducing the pulsating pressure of the refrigerant gas, and at the same time significantly reducing noise caused by refrigerant gas pulsation.

Therefore, it is not necessary to form a separate expansion space portion having a large passage sectional area outside the compressor, and even if the independent expansion space portion is provided outside the compressor, the compressor of the present invention is very compact in package size.

The foregoing embodiments are merely exemplary, and are not intended to limit the present invention. The teachings of the present invention can be readily applied to other types of devices. The description of the present invention is for illustration, not for limiting the protection scope of the claims. It will be apparent to those skilled in the art that many alternatives, modifications and variations can be made to the present invention.

Claims (10)

1. A compressor, comprising: a front case enclosing one end of the front cylinder block; a rear casing that closes one end of the rear cylinder block; a front cylinder block and a rear cylinder block arranged to interconnect between the front housing and the rear housing; a refrigerant gas inlet port and an outlet port formed on a peripheral surface of at least one of the front block and the rear block; In the front refrigerant gas absorption chamber the front discharge pipe passes through the first partition which defines the front refrigerant gas discharge chamber so as to isolate it from the front refrigerant gas absorption chamber, thereby to the The compressor externally delivers refrigerant gas discharged into the front refrigerant gas discharge chamber of the front casing; In the rear refrigerant gas absorption chamber the front discharge pipe passes through the second partition which defines the rear refrigerant gas discharge chamber so as to isolate it from the rear refrigerant gas absorption chamber, thereby to the The compressor externally delivers refrigerant gas that is discharged into the rear refrigerant gas discharge chamber of the rear housing; a front auxiliary inflation part and a rear auxiliary inflation part communicating with the outlet sides of the front exhaust pipe and the rear exhaust pipe; Exhaust connecting passages provided in the front cylinder body and the rear cylinder body and connected to the front auxiliary expansion part and the rear auxiliary expansion part; and The main expansion part is provided between the exhaust connection passages in such a manner as to communicate with the refrigerant gas outlet port. 2. The compressor according to claim 1, wherein the main expansion part extends to one end of the exhaust connection channel of the front cylinder or the rear cylinder, forming an integral body in the front cylinder or the rear cylinder. 3. The compressor according to claim 1, wherein the main expansion part is formed outside the front cylinder or the rear cylinder. 4. The compressor according to claim 1, wherein at least one or more of the front discharge pipe and the rear discharge pipe are located at a position where the refrigerant gas is discharged at the front of the front casing and the rear casing The shortest distance between the chamber and the center of the rear refrigerant gas discharge chamber and its inlet end. 5. The compressor of claim 1, wherein at least one or more of the front auxiliary expander and the rear auxiliary expander have a larger volume than the front and rear exhaust pipes. 6. The compressor according to claim 1, wherein at least one or more of the discharge connection passages have a cross-sectional area larger than or equal to the passage cross-sectional areas of the front exhaust pipe and the rear exhaust pipe. 7. The compressor according to claim 1, wherein the volume of the main expansion part is larger than or equal to the sum of the volumes of the front auxiliary expansion part and the rear auxiliary expansion part. 8. The compressor according to claim 1, wherein at least one or more of the front discharge pipe and the rear discharge pipe communicate with a lower surface of any one of the front auxiliary expansion part and the rear auxiliary expansion part. 9. The compressor according to claim 1, wherein at least one or more of the front exhaust pipe and the rear exhaust pipe has a passage cross-sectional area that becomes larger or gradually increases from the inlet to the outlet . 10. The compressor according to claim 1, wherein the length of the passage between the front exhaust pipe of the front housing and the refrigerant gas outlet end is the same as the length of the passage between the rear exhaust pipe of the rear housing and the refrigerant gas outlet end The channels are of equal length.

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