KR100279155B1 - Reciprocating piston type refrigerant compressor - Google Patents

Abstract

The refrigerant compressor of the reciprocating piston type includes a cylinder block, a drive shaft rotated together with a swash plate, a plurality of cylinder bores, a plurality of pistons disposed in the cylinder bores, front and rear valve plates, front and rear suction and discharge valves, and front and rear housings. Include. The front housing has a suction chamber for the refrigerant gas to be compressed along with the reciprocation of the plurality of pistons and a discharge chamber for the compressed refrigerant gas. The rear housing discharges the refrigerant gas of the suction chamber for the refrigerant gas to be compressed along the reciprocation of the plurality of pistons, the discharge chamber for the compressed refrigerant gas, and the discharge chamber of the front housing moved through the discharge passage formed in the cylinder block. Has an outlet chamber for In the discharge chamber of the rear housing, the discharge tube extends by a predetermined length so as to communicate with the discharge chamber at right angles. The combined volume of the discharge chamber and the discharge passage of the front housing is formed equal to the combined volume of the discharge chamber and the discharge tube of the rear housing, and the discharge tube is opposite to the inner wall from the inner wall surface of the rear housing at the point where the outlet chamber and the discharge tube communicate with each other. It extends to about half the distance to the face.

Description

Reciprocating piston type refrigerant compressor

The present invention relates to a refrigerant compressor of a reciprocating piston type suitable for use in an air conditioning system of a vehicle, and more particularly to a housing having a discharge structure capable of reducing discharge pulsation. In addition, the present invention relates to a refrigerant compressor of a reciprocating piston type which can simplify the compressor structure since a separate structure or device for maintaining the discharge tube is not required.

Compressor is a machine that compresses various working fluids so that the compressed working fluids can be used in various systems, and these compressors vary depending on the type of working fluid to be compressed, the compressive force or its use, but especially the automobile refrigeration. One of the compressors used in the apparatus is a swash plate type compressor.

Fig. 1 is a view showing a typical reciprocating piston type refrigerant compressor, and Figs. 2 and 3 respectively show a front housing and a rear housing of a conventional compressor, and the compressor has a front and rear cylinder block (1, 1a). And the front and rear cylinder blocks 1, 1a are mutually coupled in the axial direction to form a cylinder block assembly. The cylinder block assembly is received in the front housing (8) and the rear housing (9) to close both ends, and the front valve between the cylinder block assembly and the front housing (8) and the rear housing (9). The plate 10 and the rear valve plate 11 are interposed. The front housing 8 and the rear housing 9 are tightly coupled by through bolts (not shown) disposed in the through grooves 12 and 12a. The cylinder block assembly also includes a central bore 7, 7a formed axially through which the drive shaft 14 is coupled. The drive shaft 14 is provided with metal bearings 7b and 7c and lubricating oil is provided to the cylinder blocks 1 and 1a through the lubricating oil supply passages 13 and 13a.

The cylinder block assembly is provided with a plurality of cylinder bore 2, the same number of front and rear cylinder bores formed. Each cylinder bore receives a double-headed piston 4 and is reciprocated by a swash plate 3 through hemispherical shoes 6.

The swash plate 3 is accommodated in the swash plate chamber 5 by providing the swash plate chamber 5 in the cylinder block assembly. The swash plate 3 is mounted on the drive shaft 14 so that the swash plate 3 also rotates in accordance with the rotation of the drive shaft 14 due to the rotation of the electromagnetic clutch 14a, and thus the piston in the cylinder bores 2. (4) will reciprocate.

In each of the front housing 8 and the rear housing 9, a front discharge chamber 16 and a rear discharge chamber 17 are formed, and outside the front suction chamber 23 and the rear suction chamber 24 are also formed, respectively. do. The front valve plate 10 and the rear valve plate 11 have front inlets 27 and rear inlets 28, respectively, so that fluid between the intake chambers 23, 24 and the individual cylinder bores 2 can be obtained. Communication is achieved. The front valve plate 10 and the rear valve plate 11 also have a front discharge port 21 and a rear discharge port 22, respectively, so that fluid between the discharge chamber lamps 16 and 17 and the individual cylinder bores 2 can be obtained. Communication is achieved.

The inlets 27, 28 are closed by the front and rear intake valves 25, 26 in the form of reed valves that are in contact with the faces of the front and rear valve plates 10, 11, respectively. It is. The outlets 21, 22 are likewise closed by the front and rear discharge valves 19, 20 in the form of reed valves which are in contact with the surfaces of the front and rear valve plates 10, 11, respectively. The intake and discharge valves 25, 26, 19, 20 are separated from the corresponding inlets and outlets 27, 28, 21, 22 by the compression stroke of the double-headed piston 4, and thus the respective intake ports. Fields and outlets are opened.

A predetermined gap 15, 15a is formed between the outer circumferential wall of the cylinder blocks 1, 1a and the inner circumferential walls of the front and rear housings 8, 9, and the swash plate chamber 5 is formed in the cylinder blocks 1, 1a. Holes (not shown) are formed for the communication of the refrigerant with). Refrigerant introduced from the refrigerant inlet (not shown) is introduced into the refrigerant inlet chamber 43 (see FIG. 3) and formed in a valve assembly composed of the valve plate 11 and the suction and discharge valves 26 and 20. The holes are introduced into the swash plate chamber 5 through the holes (not shown) and the holes formed in the cylinder blocks 1 and 1a. The refrigerant introduced into the swash plate chamber 5 flows into the suction chambers 23 and 24 through suction holes (not shown) formed in the cylinder blocks 1 and 1a in the axial direction, and the cylinder is sucked by the piston. It is sucked into the bores 2. Discharge passages 39 and 39a are formed in the cylinder blocks 1 and 1a so as to communicate with each other on the shaft, and the refrigerant discharged into the discharge chamber 16 of the front housing 8 is rearward through the extension discharge port 40. It is moved to the discharge part 41 of the housing 9 and discharged outside the compressor through the discharge hole 42.

An O-ring 29 is provided to prevent the leakage of refrigerant when the front housing 8 and the rear housing 9 are coupled, and also a mounting lug 32 for mounting the compressor is provided. Is provided. As shown in FIGS. 2 and 3, the front housing 8 and the rear housing 9 are formed with axial bore 34, 34a and a plurality of walls 35 extending from the bosses 34b, 34c. 36) provide reinforcement and mechanical strength of the valve assembly. The inner wall 35a of the front housing 8 partitions the front suction chamber 23 and the front discharge chamber 16 and the rear suction chamber 24 is defined by the inner wall 36a and the outer wall 36b of the rear housing 9. And a rear discharge chamber 17 is formed. A discharge passage 37 is formed between the inner wall 36a and the outer wall 36b. The rear housing 9 is provided with a communication path 38 and a discharge passage 37 so that the refrigerant discharged in the discharge chamber 17 of the rear housing 9 discharges through the communication path 38 and the discharge passage 37. Through the discharge hole 42 formed in the portion 41 is discharged to the outside of the compressor. In addition, the refrigerant discharged into the discharge chamber 16 of the front housing 8 is transferred to the discharge portion 41 of the rear housing 9 through discharge passages 39 and 39a connected to the extension discharge port 40 and then discharged. It is discharged from the ball 42 to the outside of the compressor.

However, in the conventional compressor configured as described above, the discharge passage 37 for discharging the compressed refrigerant of the rear housing 9 to the outside is formed outside the discharge chamber 17 along the inner wall 36a of the discharge chamber 17. Since the discharge chamber 17 and the suction chamber 24 extend by a predetermined length, there is a problem that the discharge passage 37 must be closed by a leak preventing means such as a gasket. That is, the part of the discharge passage 37 is not closed by the rear valve plate 11 and the rear suction and discharge valves 26 and 20. Therefore, the structure is complicated, and since the discharge passage 37 is narrow and long, and has a semicircular shape, there is a problem of interrupting the refrigerant flow and causing a pressure loss.

Furthermore, since the discharge passage 37 is formed in a part of the suction chamber 24, the area of the suction chamber 24 is substantially reduced. In addition, an outer wall 36b forming a boundary between the suction chamber 24 and the discharge passage 37 communicates with the swash plate chamber 5 of the cylinder block and the suction plate 24 inside the rear housing 9. There was a problem of preventing a smooth suction of the refrigerant by closing a part of the suction ports located in the discharge passage portion of the suction ports of the).

In addition, in order to partially change the structure of the discharge passage in order to optimize the discharge passage, peripheral parts related to the discharge tube, such as a gasket, must also be changed together, resulting in a cost increase due to the change in the number of parts accompanying.

An object of the present invention is to provide a reciprocating piston type refrigerant compressor having a simplified discharge structure by forming a discharge passage in the compression chamber for discharging the refrigerant compressed from the compression chamber of the rear housing to the outside of the compressor.

According to the characteristics of the present invention it is easy to change the design of the compression chamber of the compressor, and the suction and discharge of the refrigerant is made smoothly to reduce the pressure loss generated during the suction and discharge.

Still another object of the present invention is to provide a reciprocating piston type refrigerant compressor having a discharge structure capable of solving the problem of noise caused by gas pulsation generated in a conventional refrigerant compressor. The object of the present invention is to maintain the same volume of the discharge chamber of the front housing and the rear housing, the discharge pressure waveform of the refrigerant gas discharged to the discharge chamber of the rear housing is the discharge pressure waveform of the refrigerant gas discharged to the discharge chamber of the rear housing By having a phase difference of about 180 ° with the discharge pressure waveforms, the noise problem due to the pulsation of the gas refrigerant can be solved.

A reciprocating piston type refrigerant compressor according to the present invention comprises: a cylinder block having a shaft bore formed in the center and a plurality of cylinder bores arranged around the shaft bore;

A drive shaft rotatably supported by the shaft bore and rotated together with the swash plate by supporting the swash plate;

A plurality of pistons operatively coupled to the swash plate to reciprocate in the plurality of cylinder bores to allow suction, compression and discharge of refrigerant gas in accordance with rotation of the drive shaft and the swash plate;

Front and rear valve plate means respectively covering the ends of the cylinder bores at both ends of the cylinder block and having a plurality of inlets and a plurality of outlets for intake and discharge of refrigerant gas to and from each of the cylinder bores;

An inner wall and the front valve plate means for closing one end of the cylinder block and defining a front discharge chamber for receiving compressed refrigerant gas discharged from the plurality of cylinder bores through the plurality of discharge holes formed in the front valve plate means. A front housing having a front suction chamber defined by said inner wall and an inner surface for accommodating refrigerant gas to be compressed through said plurality of suction ports;

An inner wall for closing the other end of the cylinder block and defining a rear discharge chamber for receiving compressed refrigerant gas discharged from the plurality of cylinder bores through the plurality of discharge holes formed in the rear valve plate means, the rear valve plate Through a rear suction chamber defined by the inner wall and the inner surface, a discharge tube disposed inside the rear discharge chamber, and a discharge passage formed in the cylinder block to receive refrigerant gas to be compressed through the plurality of suction ports formed in the means; A rear housing having an outlet chamber for outflowing the refrigerant gas of the front discharge chamber of the moved front housing;

It has a plurality of reed valves, disposed between the cylinder block and the front valve plate means for the front suction and discharge valve means for communication of the refrigerant gas between the front suction chamber and the discharge chamber of the front housing and the cylinder bores ; And

A rear suction and discharge valve means having a plurality of reed valves, disposed between the cylinder block and the rear valve plate means for communication of refrigerant gas between the rear suction chamber and the discharge chamber of the rear housing and the cylinder bores. It includes;

1 is a longitudinal sectional view of a typical compressor;

2 is a front view of a front housing of a conventional compressor;

3 is a front view of a rear housing of a conventional compressor.

4 is a longitudinal sectional view of a compressor according to an embodiment of the present invention;

5 is a front view of the front housing of the compressor according to the present invention;

6 is a front view of the rear housing of the compressor according to the present invention;

Figure 7 is a front view of the front housing of the present invention with a valve plate, suction and discharge valves.

Figure 8 is a front view of the rear housing of the present invention with a valve plate, suction and discharge valves.

Fig. 9 is a front view of the rear housing showing the cutting tube cutting ratio formed in the rear housing;

10 is a waveform diagram of a refrigerant discharged to the discharge chamber of the front housing of the compressor of the present invention;

11 is a waveform diagram of a refrigerant discharged to the discharge chamber of the rear housing of the compressor of the present invention;

Fig. 12 is a waveform diagram showing superimposed waveforms of refrigerant discharged in the discharge chambers of the front and rear housings of the compressor of the present invention;

FIG. 13 is a graph showing the rotational speed of the compressor versus the pulsating pressure of the refrigerant according to the discharge tube cutting ratio of FIG.

Hereinafter, a configuration according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

4 is a cross-sectional view of the compressor according to the present invention, FIG. 5 is a front view of the compressor front housing according to the present invention, FIG. 6 is a front view of the rear housing of the compressor according to the present invention, and FIGS. 7 and 8 are valve plates respectively. Is a front view of a front housing and a rear housing of the present invention having suction and discharge valves. 9 is a front view of the rear housing showing the rate of cutting the discharge pipe formed in the rear housing.

The refrigerant compressor of the reciprocating piston type according to the present invention has a front cylinder block 50 and a rear cylinder block 51, which cylinder blocks 50, 51 are mutually coupled axially to form a cylinder block assembly. The cylinder block assembly is housed in the front housing 58 and the rear housing 59, and the front and rear valve plates 60, 61 and the housings interposed between the cylinder block assembly and the front and rear housings 58, 59. 58, 59) both ends are closed. Through grooves 62 and 62a are formed in the front and rear housings 58 and 59 and the front and rear cylinder blocks 50 and 51 so as to be tightly coupled by the through bolts 64. The coupled cylinder blocks 50, 51 also have axially formed center bores 57, 57a, to which the drive shaft 65 is coupled. Metal bearings 57b and 57c are coupled around the drive shaft to facilitate rotation of the drive shaft.

The cylinder block assembly is provided with a plurality of cylinder bores 52, for example five front cylinder bores and five rear cylinder bores provided coaxially. These cylinder bores are arranged spaced apart at equal intervals around the drive shaft 65. Ten cylinder bores 52 are provided with two double head pistons 53, which are engaged with the swash plate 54 by hemispherical shoes 56. The pistons 53 are linearly reciprocated by the swash plate 54 in accordance with the rotation of the drive shaft 65 by the rotation of the electromagnetic clutch 14a.

The swash plate 54 is accommodated in the swash plate chamber 55 by providing the coupled cylinder blocks 50 and 51 with the swash plate chamber 55. The swash plate 54 is mounted on the drive shaft 65 so that the swash plate 54 also rotates in accordance with the rotation of the drive shaft 65, so that the two head pistons 53 in the cylinder bores 52 reciprocate. Done. As each piston 53 in the cylinder bores 52 reciprocates, suction and discharge of the refrigerant gas occur.

The front discharge chamber 68 and the rear discharge chamber 69 are formed in each of the front housing 58 and the rear housing 59, and the front suction chamber 74 and the rear suction chamber 75 are respectively formed outside the front housing 58 and the rear housing 59. . The front valve plate 60 and the rear valve plate 61 have front inlets 78 and rear inlets 79, respectively, between the suction chambers 74, 75 and the individual cylinder bores 52. Fluid communication is achieved. The front valve plate 60 and the rear valve plate 61 also have a front discharge port 72 and a rear discharge port 73, respectively, so that fluid between the discharge chambers 68 and 69 and the individual cylinder bores 52 can be obtained. That is, the inlets 78 and 79 are compressed by the compression stroke of the two pistons 53 by causing the low pressure refrigerant gas to flow into the respective cylinder bores 52. The discharge ports 72 and 73 allow the high pressure compressed refrigerant gas to be discharged from the cylinder bores 52 to the discharge chambers 68 and 69 by the compression stroke of the double head piston 53.

The inlets 78 and 79 respectively have front and rear suctions with reed valves 76a and 77a which are in contact with the inner surfaces of the front and rear valve plates 60 and 61, ie the surfaces which contact the cylinder block assembly. It is closed by valves 76 and 77. Similarly, the outlets 72, 73 are in contact with the outer surfaces of the front and rear valve plates 60, 61, that is, the surfaces that contact the front and rear housings 58, 59, and the reed valves 70a, 71a. It is closed by the front and rear discharge valves (70, 71) having. The reed valves 76a, 77a, 70a and 71a of the intake and discharge valves 76, 77, 70 and 71 are respectively corresponding to the inlets 78 and 79 and the discharge port by the reciprocating motion of the double-headed piston 53. Spaces from the holes 72 and 73, thereby opening the respective inlets and outlets.

Between the outer circumferential surface of the cylinder blocks 50 and 51 and the inner circumferential surface of the front and rear housings 58 and 59, predetermined gaps 67 and 67a are formed, and the outer peripheral walls of the cylinder blocks 50 and 51 are cut out. Portions (not shown) are provided. Since some of the through holes 62 and 62a to which the through bolts 64 are fastened are formed larger than the diameter of the through bolts, the suction passage is moved in the axial direction for the movement of the refrigerant gas in the state where the through bolts are fastened. It is formed in the cylinder blocks (50, 51). Similar holes are formed in the valve plates 60 and 61 and the suction valves 76 and 77 corresponding to the suction passages formed in the cylinder blocks 50 and 51. The suction passage is thus in communication with the front and rear suction chambers 74 and 75 of the front and rear housings 58 and 59. Of course, the suction passage may be separately formed in the cylinder blocks 50 and 51 without using the through grooves. Accordingly, the refrigerant flowing from the refrigerant inlet 96 flows into the swash plate chamber 55 through the cut portions of the cylinder blocks 50 and 51. The refrigerant introduced into the swash plate chamber 55 is sucked into the front suction chamber 74 and the rear suction chamber 75 of each of the front housing 58 and the rear housing 59 through the suction passage. Then, by the compression stroke of the pistons 53, the reed valves 76a, 77a of the front and rear suction valves 76, 77 are opened as shown in Figs. Refrigerant gas is sucked into the bore.

5 and 6, the front inner wall 82 of the polymorph is formed in the center part of the bottom face of the front housing 59 which has a predetermined thickness and protrudes upwards from the bottom face. This front inner wall 82 extends by a predetermined length and comes into contact with the front valve plate 60 (preferably a valve assembly consisting of a front intake valve, a front discharge valve, a gasket and a front valve plate) on its upper surface. At one end of the front inner wall 82, a transfer discharge port 91 extends from the front inner wall 82. The front discharge chamber 68 and the front suction chamber 74 are provided by the front inner wall 82 and the inner circumferential wall of the front housing 58.

In the central portion of the bottom surface of the rear housing 59, a polymorphic rear inner wall 83 is formed which has a predetermined thickness and projects upward from the bottom surface. This rear inner wall 83 extends by a predetermined length and comes into contact with the rear valve plate 61 (preferably a valve assembly consisting of a rear intake valve, a rear discharge valve, a gasket and a rear valve plate) on its upper surface. An extension 93 is formed at one end of the rear inner wall 83. The rear discharge chamber 69 and the rear suction chamber 75 are provided by the inner wall of the rear inner wall 83 and the rear housing 59. In the discharge chamber 69 of the rear housing 59, a discharge tube 89 communicating with the discharge chamber 92 is formed to discharge the refrigerant gas discharged into the discharge chamber 69 to the outside of the compressor. One end of the tube 89 extends in the discharge chamber 69 by a predetermined length and the other end is connected to the outlet chamber 92.

Referring again to FIGS. 4, 5, 6, 7, and 8, the refrigerant gas introduced through the refrigerant inlet 96 is introduced into the swash plate chamber 55, and then the front and rear suction chambers 74 and 75 through the suction passages. Inhaled). The refrigerant gas stored in the suction chambers 74, 75 opens and closes the reed valves 76a, 77a of the front and rear suction valves 76, 77 according to the reciprocating motion of the piston 53, and thus the front and rear suction ports. It is sucked into the individual cylinder bores 52 via 78, 79. The refrigerant gas compressed by the compression stroke of the piston 53 is individually passed through the front and rear discharge ports 72 and 73 by opening and closing the reed valves 70a and 71a of the front and rear discharge valves 70 and 71. It discharges from the cylinder bore 52 to the front and rear discharge chambers 68 and 69. The refrigerant gas discharged into the discharge chamber 69 of the rear housing 59 is discharged to the outside of the compressor through the discharge chamber 89 and the discharge chamber 92 and the discharge hole 98 through the discharge tube 89. Meanwhile, the refrigerant gas discharged into the discharge chamber 68 of the front housing 58 flows out of the rear housing 59 through the discharge discharge port 91 and the discharge passage 90 formed in the cylinder blocks 50 and 51. Are transferred to 92. Since the outlet chamber 92 communicates with the discharge hole 98, the refrigerant gas transferred to the outlet chamber 92 is discharged to the refrigerant outlet 97 through the discharge hole 98.

In the compressor of the present invention, the volume of the discharge chamber 68 of the front housing 58 corresponds to the discharge chamber 69 of the rear housing 59 so as to match the volume of the discharge chamber 69 of the rear housing 59. do. More preferably, the combined volume of the discharge chamber 68 and the discharge passage 90 of the front housing 58 is equal to the combined volume of the discharge chamber 69 and the discharge tube 89 of the rear housing 59. .

The discharge tube 89 formed in the rear housing 59 may extend to have an arbitrary length in the discharge chamber 69. The discharge chamber 69 is formed on the same extension line as the discharge hole 98 and the discharge chamber 92. Is formed. One end of the discharge tube 89 communicates with the outlet chamber 92 at right angles, and the other end is opened. In addition, the length of the discharge tube 89 in the discharge chamber 69 is also directly related to the pulsation noise, and the inner wall at the point where the discharge chamber 92 of the rear housing 59 and the discharge tube 89 communicate with each other ( It is preferable to extend the discharge tube 89 to a point corresponding to about 1/2 of the distance from the inner surface of the inner surface 83 to the opposite surface of the inner wall 83. In other words, the distance between the point A where the center line is in contact with the inner surface of the rear inner wall 83 and the point A connecting the extension 93 with respect to the center line of the discharge tube 89 is defined as L. In this case, the extension length of the discharge tube 89 can be determined in relation to this L. As can be seen from Figs. 7 to 11, the pressure waveform of the refrigerant gas discharged to the discharge chamber 68 of the front housing 58 when the discharge tube 89 is extended to the point C half of L is formed. The pressure waveforms of the refrigerant gas discharged to the discharge chamber 69 of the rear housing 59 are almost the same in shape, and the phase difference is almost opposite. As a result, the pressure waveforms of the refrigerant gas discharged to the discharge chamber 69 of the rear housing 59 overlap each other and cancel each other with the pressure waveforms of the refrigerant discharged to the discharge chamber 68 of the front housing 58.

10 to 12, FIG. 10 shows the pressure waveform of the refrigerant gas discharged to the discharge chamber 68 of the front housing 58, and FIG. 11 is discharged to the discharge chamber 69 of the rear housing 59. The pressure waveform of the refrigerant gas is shown. Since the two pressure waveforms have almost the same shape while the phase difference is maintained at approximately 180 °, when the two pressure waveforms overlap each other, the pulsation noise is remarkably reduced because they cancel each other due to the interference phenomenon (see FIG. 12). Thus, when the pulsation waveforms are superimposed, the mutually canceling of the discharge chamber 68 and the discharge passageway 90 of the front housing 58 of the discharge chamber 69 and the discharge tube 89 of the rear housing 59 is offset. Because it is the same as collective. That is, in the reciprocating piston type refrigerant compressor, once the compressor is driven, the pressure waveform of the refrigerant gas discharged into the discharge chamber of the front housing 58 and the pressure waveform of the refrigerant gas discharged into the discharge chamber of the rear housing 59 are almost 180 degrees. It has a phase difference of °. The refrigerant gas discharged to the discharge chamber 68 of the front housing 58 is moved to the discharge chamber 92 of the rear housing 59 through the discharge passage 90, where the discharge tube 89 of the rear housing 59 is discharged. Refrigerant gas flowing into the outlet chamber 92 through the () is mixed with each other to cancel the refrigerant pressure waveform having a phase difference of 180 °.

In addition, in the swash plate type compressor, the refrigerant compressed through the plurality of cylinders is discharged in the same amount alternately to the discharge chambers 68 and 69 of each of the front housing 58 and the rear housing 59. Therefore, the amount of refrigerant gas transferred to the outlet chamber 92 of the rear housing 59 through the discharge tube 89 of the rear housing 59 is transferred from the discharge chamber 68 of the front housing 58 to the discharge outlet 91. And the amount of the refrigerant gas transferred to the outlet chamber 92 through the discharge passage 90.

Through the circulation of the refrigerant, a certain amount of refrigerant is present in equilibrium in the discharge chambers 68 and 69.

FIG. 13 is a graph showing the rotational speed of the compressor versus the pulsation pressure of the refrigerant according to the discharge tube cutting ratio of FIG. 9, in which the discharge tube 89 formed in the discharge chamber 69 of the rear housing 59 is formed by the length L; It is shown based on the actual test data, making one thing into 0.0% and cutting what formed to the point B 100%. As shown in Fig. 11, the smallest pulsation pressure appears when 50% of the length L is cut. Thus, it can be seen that the pulsation noise is substantially eliminated in comparison with the pulsation pressure data for the compressors of the prior art in the graph.

The present invention constituted as described above can simplify the structure of the housing because the discharge pipe is configured inside the rear housing, and incur a cost increase because it does not affect parts other than the rear housing even when the rear housing is changed. I never do that. In addition, the discharge pipe does not interfere with the suction chamber space of the rear housing as compared with the conventional, it is possible to facilitate the suction of the refrigerant.

In addition, since the pulsation of the refrigerant gas discharged from the discharge chamber of the rear housing overlaps with the pulsation of the refrigerant gas discharged from the front housing, the pulsation pressure, that is, the noise due to the pulsation can be minimized, and the discharge pipe is formed in a straight pipe shape. Since the discharge pressure is not lost, it is possible to smoothly discharge the compressed refrigerant.

Claims (5)

A cylinder block having a shaft bore formed in the center and a plurality of cylinder bores arranged around the shaft bore; A drive shaft rotatably supported by the shaft bore and rotated together with the swash plate by supporting the swash plate; A plurality of pistons operatively coupled to the swash plate to reciprocate in the plurality of cylinder bores to allow suction, compression and discharge of refrigerant gas in accordance with rotation of the drive shaft and the swash plate; Front and rear valve plate means respectively covering the ends of the cylinder bores at both ends of the cylinder block and having a plurality of inlets and a plurality of outlets for intake and discharge of refrigerant gas to and from each of the cylinder bores; An inner wall and the front valve plate means for closing one end of the cylinder block and defining a front discharge chamber for receiving compressed refrigerant gas discharged from the plurality of cylinder bores through the plurality of discharge holes formed in the front valve plate means. A front housing having a front suction chamber defined by said inner wall and an inner surface for accommodating refrigerant gas to be compressed through said plurality of suction ports; An inner wall for closing the other end of the cylinder block and defining a rear discharge chamber for receiving compressed refrigerant gas discharged from the plurality of cylinder bores through the plurality of discharge holes formed in the rear valve plate means, the rear valve plate Through a rear suction chamber defined by the inner wall and the inner surface, a discharge tube disposed inside the rear discharge chamber, and a discharge passage formed in the cylinder block to receive refrigerant gas to be compressed through the plurality of suction ports formed in the means; A rear housing having an outlet chamber for outflowing the refrigerant gas of the front discharge chamber of the moved front housing; It has a plurality of reed valves, disposed between the cylinder block and the front valve plate means for the front suction and discharge valve means for communication of the refrigerant gas between the front suction chamber and the discharge chamber of the front housing and the cylinder bores ; And A rear suction and discharge valve means having a plurality of reed valves, disposed between the cylinder block and the rear valve plate means for communication of refrigerant gas between the rear suction chamber and the discharge chamber of the rear housing and the cylinder bores. Refrigerant compressor of the reciprocating piston type comprising; The method of claim 1, By forming the volume of the front discharge chamber of the front housing and the volume of the rear discharge chamber of the rear housing the same, the pressure waveform of the refrigerant gas discharged to the front housing and the pressure waveform of the refrigerant gas discharged to the rear housing are mutually different. A reciprocating piston type refrigerant compressor having a substantially opposite phase difference, wherein the discharge tube and the outlet chamber communicate with each other at substantially right angles so that the pressure waveforms of the front and rear housings cancel each other in the outlet chamber to substantially eliminate pulsation noise. . The method of claim 1, The combined volume of the front discharge chamber and the discharge passage of the front housing is the same as the combined volume of the rear discharge chamber and the discharge tube of the rear housing to discharge the pressure waveform of the refrigerant gas discharged to the front housing and the rear housing. The pressure waveforms of the refrigerant gases are approximately 180 ° out of phase with each other, and the discharge tube and the outlet chamber communicate with each other at right angles to each other so that the pressure waveforms of the front and rear housings cancel each other in the outlet chamber of the rear housing. A reciprocating piston type refrigerant compressor that substantially eliminates pulsation noise. The method of claim 2, The discharge pipe of the rear housing extends to a point corresponding to about 1/2 of the distance from the inner surface of the inner wall of the rear housing to the opposite surface of the inner wall at the point where the outlet chamber and the discharge tube communicate with each other. Piston type refrigerant compressor. The method of claim 3, The discharge pipe of the rear housing extends to a point corresponding to about 1/2 of the distance from the inner surface of the inner wall of the rear housing to the opposite surface of the inner wall at the point where the outlet chamber and the discharge tube communicate with each other. Piston type refrigerant compressor.