JP3487088B2 - Muffler structure of compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor applied to, for example, a vehicle air conditioning system, and more particularly to a muffler structure of the compressor.

[0002]

2. Description of the Related Art As a compressor of this type, there is, for example, one having the following structure. That is, the housing that houses the compression mechanism is configured by integrally joining and fixing a plurality of housing components with through bolts.
The muffler portions are integrally formed with the outer shells of the adjacent housing components so that their openings face each other.
Therefore, the inner spaces of both muffler parts are integrated at the same time as the housing structure is joined, and a muffler space is formed between both muffler parts. The gasket is interposed between the muffler parts to seal the joint surface. The pressure pulsation of the refrigerant gas sucked by the compression mechanism or the refrigerant gas discharged by the compression mechanism is attenuated by passing through the muffler space. Therefore, vibration and noise caused by the pressure pulsation of the refrigerant gas are reduced.

[0003]

However, the compressor is vibrated by the operation of the compression mechanism and external factors. Further, the inside of the muffler space becomes a high-pressure atmosphere by introducing the suction gas or the discharge gas having a pressure higher than the atmospheric pressure. The gasket has a thin plate shape and low tensile strength, and is deformed when a slight displacement movement at the joint portion of the housing constituent body due to the above-mentioned vibration or stress is applied by the high pressure in the muffler space, and it is displaced from a predetermined position and sealed. There was a risk that the stopping function would not be maintained.

The present invention has been made in view of the problems existing in the above-mentioned prior art, and its purpose is to prevent the displacement of the muffler gasket for sealing the joint surface of the muffler. To provide a possible compressor muffler structure.

[0005]

In order to achieve the above object, according to the invention of claim 1, both muffler parts are provided by providing muffler parts in the outer shell parts of the adjacent housing components so that their openings are opposed to each other. While forming a muffler space between them,
A muffler gasket for sealing the joint surface of the muffler is provided, the inner peripheral edge of the gasket is bridged by an arm so as to cross the muffler space, and the through bolt is connected to the arm at the gasket. It is a muffler structure penetrated near the base of.

According to the invention of claim 2, the muffler gasket includes a plurality of arms. According to the third aspect of the invention, the muffler gasket is provided with a partition part for partially partitioning the muffler space by closing the opening area defined by the arm part.

In the invention of claim 4, the muffler gasket is integrally extended from the housing gasket that seals the joint surface of the housing structure. According to the invention of claim 5, the partition portion is provided at a position facing the entrance of the muffler space.

According to the invention of claim 6, the arm portion
Position where the partitioned opening area faces the entrance of the muffler space
It was installed in. In the invention of claim 7, the compression mechanism includes a cylinder bore formed in a cylinder block that is a housing structure, and a double-headed piston housed in the cylinder bore and reciprocated, and one piston end surface is provided. The discharge gas discharged from the compression chamber formed surrounded by the cylinder bore and the discharge gas discharged from the compression chamber formed surrounded by the other piston end surface and the cylinder bore join together in the muffler space. The discharge gas inlet from one compression chamber side and the discharge gas inlet from the other compression chamber side are arranged to face each other in the muffler space.

(Operation) In the invention of claim 1 having the above-mentioned configuration, the cycle of suction, compression and discharge of the refrigerant gas and the like is performed by the operation of the compression mechanism. The refrigerant gas sucked by the compression mechanism and / or the refrigerant gas discharged by the compression mechanism is passed through the muffler space. Therefore, the pressure pulsation of the gas is attenuated, and the vibration and noise caused by it are suppressed.

Here, the compressor is vibrated by the operation of the compression mechanism and external factors. Further, the inside of the muffler space becomes a high-pressure atmosphere by introducing the suction gas or the discharge gas having a pressure higher than the atmospheric pressure. However, the inner peripheral edge of the muffler gasket is connected by bridging by the arm so as to cross the muffler space, so that the tensile strength is enhanced. Further, the through bolt for joining and fixing the housing structure directly penetrates the vicinity of the base portion of the arm portion to directly support the arm portion. Therefore, the gasket for the muffler portion has a small amount of deformation even when the above-mentioned vibration and stress due to the high pressure in the muffler space act, and the deviation from the predetermined sealing position can be suppressed as much as possible.

Further, the refrigerant gas flowing into the muffler space is disturbed by a part of the refrigerant gas colliding with the arm portion, and the damping effect of the pressure pulsation is enhanced. In the invention of claim 2, the muffler gasket has a plurality of arms, so that the tensile strength is further enhanced.

According to the third aspect of the present invention, the inside of the muffler space is partly divided by the partitioning portion and its shape is complicated, so that the pressure pulsation of the refrigerant gas is damped more effectively.

In the invention of claim 4, the muffler portion gasket is integrally extended from the housing gasket that seals the joint surface of the housing structure. Therefore, the number of parts can be reduced as compared with the case where both are provided separately.

In the invention of claim 5, the refrigerant gas flowing into the muffler space directly collides with the partition portion, and the pressure pulsation of the refrigerant gas is damped more effectively. In claim 6, the opening sectioned by the arm portion is used.
The mouth area is provided at a position facing the entrance of the muffler space
In particular, in the invention of claim 7, one compression chamber
From the discharge gas discharged from the other compression chamber
Directly with the discharged gas through the open area.
U Therefore, the pressure pulsation of the discharge gas is effectively damped.
It

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION First and second embodiments of the present invention will be described below. (First Embodiment) The present embodiment is embodied in a discharge muffler structure of a double-headed piston type compressor.
That is, as shown in FIGS. 1 to 3, the pair of cylinder blocks 11A and 11B are joined to each other at the opposite end edges. The housing gasket (hereinafter, simply referred to as a gasket) 51 includes both cylinder blocks 11A and 1A.
It is interposed between 1B and seals the joint surface. Although not described in detail, the gasket 51 is configured by covering a thin metal plate with a sealing member such as synthetic rubber. The front housing 12 is joined to the front end surface of the front side cylinder block 11A via the front side valve forming body 13. The rear housing 14 is joined to the rear end surface of the rear cylinder block 11B via the rear valve forming body 15. The valve forming bodies 13 and 15 include a front housing 12 and a front cylinder block 1.
1A or has a function of sealing the joint surface between the rear cylinder block 11B and the rear housing 13. In the present embodiment, the cylinder blocks 11A, 1
1B, front housing 12 and rear housing 14
However, each is a housing structure.

The plurality of first bolt insertion holes 16 extend from the front housing 12 through the front side valve forming body 13, the front side cylinder block 11A, the gasket 51, the rear side cylinder block 11B and the rear side valve forming body 15 to the rear side. It is provided in the housing 14. The same number of the first through bolts 17 are inserted into the first bolt insertion holes 16 from the front housing 12 side, and the first housing bolts 17a of the rear housing 14 are formed by the threaded portions 17a formed at the tips thereof.
The bolt insertion hole 16 is screwed into a screw hole 16a. The front housing 12 and the rear housing 14 are fastened and fixed to the end surfaces of the corresponding cylinder blocks 11A and 11B by the first through bolts 17.

The drive shaft 18 is the cylinder block 11 described above.
It is rotatably supported at the centers of A and 11B and the front housing 12 via a pair of radial bearings 19. The lip seal 20 is interposed between the outer periphery of the front end of the drive shaft 18 and the front housing 12. The drive shaft 18 is operatively connected to an external drive source such as a vehicle engine via a clutch mechanism (not shown), and when the clutch mechanism is connected, the drive force of the external drive source is transmitted and rotationally driven.

A plurality of cylinder bores 21 are provided in the drive shaft 1.
8 so that each cylinder block 11A,
Penetrations are formed between both ends of 11B on the same circumference at predetermined intervals. The same number of double-headed pistons 22 are reciprocally fitted and supported in the respective cylinder bores 21, and the compression chambers 23 (front side) are provided in the respective cylinder bores 21 between their end faces and the valve forming bodies 13 and 15. ), 24 (rear side) are formed in plural.

The crank chamber 25 is defined inside the middle of the two cylinder blocks 11A and 11B. The swash plate 26 is fitted and fixed to the drive shaft 18 in the crank chamber 25, and the outer peripheral portion of the swash plate 26 is connected to the piston 2 via the shoe 27.
It is moored in the middle of 2. And the piston 22
Are reciprocated through the swash plate 26 by the rotation of the drive shaft 18. The pair of thrust bearings 28 are interposed between both end faces of the swash plate 26 and the inner end faces of the cylinder blocks 11A and 11B, and the swash plate 26 is interposed between the cylinder blocks 11A and 11B via the thrust bearing 28. It is sandwiched and held. The crank chamber 25 is connected to an external refrigerant circuit (not shown) via the suction port 50 and constitutes a suction pressure region.

Front suction chamber 29 and rear suction chamber 3
0 is partitioned and formed in the center part in the front housing 12 and the rear housing 14. The intake passage 31 includes both cylinder blocks 11A, 11B and the valve forming body 13,
The front suction chamber 29 and the rear suction chamber 30 are connected to the crank chamber 25.
The front-side discharge chamber 32 and the rear-side discharge chamber 33 are partitioned and formed in an annular shape in the outer peripheral portions of the front housing 12 and the rear housing 14.

A plurality of suction holes 34 are provided in each cylinder bore 21.
Correspondingly, the valve forming bodies 13 and 15 are penetrated. The suction valve 35 is formed in each of the valve forming bodies 13 and 15 and opens and closes each suction hole 34. Then, the suction valve 35 is opened as the piston 22 moves from the top dead center position to the bottom dead center position, and the refrigerant gas is sucked into the compression chambers 23, 24 from both suction chambers 29, 30.

A plurality of discharge holes 36 are provided so as to correspond to each cylinder bore 21 in each of the valve forming bodies 13 and 15. The discharge valve 37 is formed in each of the valve forming bodies 13 and 15, and opens and closes each discharge hole 36. The discharge valve 37 is moved along with the movement of the piston 22 from the bottom dead center position to the top dead center position.
By this action, the refrigerant gas in each compression chamber 23, 24 is compressed to a predetermined pressure and discharged into both discharge chambers 32, 33. In addition, the opening degree of the discharge valve 37 is determined by the valve forming bodies 13, 1
5 is provided by a retainer 38.

Next, the muffler structure of the double-headed piston type compressor having the above construction will be described. As shown in FIGS. 1 to 3, the front muffler portion 41A is integrally formed on the outer shell of the front cylinder block 11A, and the rear muffler portion 41B is integrally formed on the outer shell of the rear cylinder block 11B. The inner space of both muffler parts 41A and 41B is opened toward the muffler parts 41B and 41A facing each other. The inner space of both muffler parts 41A and 41B is integrated by joining both cylinder blocks 11B and 11A, and the muffler space 42 straddling both muffler parts 41A and 41B is integrated.
Is formed. The muffler parts 41A and 41B are
The cylinder blocks 11A and 11B are extended in the circumferential direction in order to obtain a predetermined volume of the muffler space 42, and the degree of outward protrusion of the cylinder blocks 11A and 11B is reduced as much as possible. Also, the muffler space 42
Forming the muffler portion 41A, 41B across both to increase the volume thereof also contributes to reducing the degree of protrusion of the muffler portion 41A, 41B from the cylinder blocks 11A, 11B.

The plurality of (two) second bolt insertion holes 43 are
The outer peripheral side meat portion of the front side muffler portion 41A is vertically penetrated and formed in the outer peripheral side meat portion of the rear side muffler portion 41B. The same number (two) of second bolts 44 as through bolts are
The front side muffler portion 41 with respect to the second bolt insertion hole 43
The screw portion 44a inserted from A and formed at the tip thereof
As a result, the second bolt insertion hole 43 of the rear muffler portion 41B is provided.
Is screwed into a screw hole 43a formed in a part of. Due to the presence of the second through bolts 44, the cylinder blocks 11A and 11B ensure more reliable joining between the muffler portions 41A and 41B.

Both of the discharge chambers 32 and 33 are provided in each valve forming body 1.
The muffler space 42 is communicated with the muffler space 42 through communication passages 46 and 47 that extend through the cylinder blocks 3 and 15 from the cylinder blocks 11A and 11B, respectively. Both passages 46, 47
Are arranged so that the inlets 46a and 47a to the muffler space 42 are opposed to each other in the muffler space 42. The outlet 48 as the outlet of the muffler space 42 is
The muffler space 41 is formed in the rear muffler portion 41B, and the muffler space 42 communicates with an external refrigerant circuit through the discharge port 48. Therefore, the linear distance from the inlet 46a to the outlet 48 and the linear distance from the inlet 47a to the outlet 48 are unequal lengths (the linear distance from the inlet 46a to the outlet 48 is longer). .

The muffler sealing portion 52 serving as a muffler gasket includes a portion of the gasket 51 and a muffler space 42.
It is configured by integrally extending to the side. The joint surface of the muffler parts 41A and 41B is sealed by the interposition of the muffler sealing part 52. The inner peripheral edge portion 52 a of the muffler sealing portion 52 surrounds the muffler space 42 in an annular shape substantially along the inner peripheral surface of the muffler space 42. And
In the present embodiment, the two arm portions 53A, 53B
Are extended integrally with the muffler sealing portion 52 so as to traverse the muffler space 42, respectively, and the arm portion 53 is provided.
The inner peripheral edge portion 52a of the muffler sealing portion 52 by A and 53B.
Are bridged and connected. Therefore, the muffler sealing portion 52
In, the opening area 54 surrounded by the inner peripheral edge portion 52a is plural (three) by both arm portions 53A and 53B.
Are divided into open areas 54a to 54c. In addition, on the line opposite to the entrances 46a and 47a to the muffler space 42,
There is an opening area 54a.

The two second through bolts 44 have corresponding arm portions 53A, 5 in the muffler sealing portion 52, respectively.
It penetrates near the base of 3B. In other words, the muffler sealing portion 52 of the gasket 51 has the inner peripheral edge portion 5
Through holes 52b that allow passage of the second through bolts 44 are provided near the bases of the arm portions 53A and 53B that bridge the 2a.

Next, the operation of the double-headed piston type compressor having the above construction will be described. Now, when the driving force is transmitted from the external drive source such as the vehicle engine to the drive shaft 18 due to the connection of the clutch mechanism, the reciprocating motion of the piston 22 is started in association with the rotation of the swash plate 26. When the reciprocating motion of the piston 22 is started, in the compression chambers 23 and 24, the piston 22
Along with the reciprocating movement of the refrigerant gas, suction of the refrigerant gas from the suction chambers 29, 30, compression in the compression chambers 23, 24, and discharge chamber 32,
The discharge cycle to 33 is started.

The discharge gas discharged to the front and rear discharge chambers 32 and 33 flows into the muffler space 42 through the communication passages 46 and 47, respectively. Same muffler space 42
The discharge gas flowing in is discharged toward the external refrigerant circuit via the discharge port 48. The discharge gas is the muffler space 4
By passing through 2, the pressure pulsation component is reflected and interfered in the muffler space 42, and the pressure pulsation of the discharge gas discharged toward the external refrigerant circuit is attenuated and becomes small.

The present embodiment having the above-mentioned structure has the following effects. (1) The inner peripheral edge portion 52a of the muffler sealing portion 52 is provided with the arm portion 53 provided so as to cross the inside of the muffler space 42.
The tensile strength is enhanced by being bridged by A and 53B. In addition, the second through bolt 44 penetrates in the vicinity of the bases of the arm portions 53A and 53B, and
Directly support. Therefore, the muffler sealing portion 52
Is less likely to be deformed even if stress acts due to the displacement of the cylinder blocks 11A and 11B and the high pressure in the muffler space 42, and the joint surfaces of the muffler portions 41A and 41B can be reliably sealed.

Further, the discharge gas flowing into the muffler space 42 is disturbed when a part of the discharge gas collides with the arm portions 53A and 53B, and the damping effect of the pressure pulsation is enhanced.

(2) The muffler sealing portion 52 has a plurality of arm portions 53A and 53B. Therefore, the tensile strength of the muffler sealing portion 52 is further increased. Moreover, the flow of the discharge gas in the muffler space 42 is further disturbed. Therefore, the above-mentioned effect (1) is more effectively exhibited.

(3) The muffler sealing portion 52 is formed integrally with the housing gasket 51. Therefore, both 5
The number of parts can be reduced as compared with the case where 1, 52 are separately provided. As a result, the number of assembling steps of the compressor can be reduced, and the manufacturing cost can be reduced.

(4) The discharge gas inlet 46a from the front side discharge chamber 32 to the muffler space 42 and the rear side discharge chamber 33.
The inlet 47a from the opening part 5 of the muffler sealing part 52
It is directly opposed via 4a. Therefore, the discharge gas flowing from the front discharge chamber 32 into the muffler space 42 and the discharge gas flowing from the rear discharge chamber 33 directly collide with each other in the muffler space 42. As a result, mutual pressure pulsation components interfere with each other, the flow velocity in the muffler space 42 is weakened, and the pressure pulsation of the discharge gas discharged from the discharge port 48 toward the external refrigerant circuit is effectively attenuated. .

(5) The straight line distance from the inlet 46a to the discharge port 48 and the straight line distance from the inlet 47a to the discharge port 48 are unequal lengths. As described above, by making the passage length of the discharge gas from one side and the passage length of the discharge gas from the other side in the muffler space 42 different, the pressure pulsation of both discharge gases in the muffler space 42 is made. The reflection and interference of the components are effectively performed. As a result, the pressure pulsation of the discharge gas discharged from the muffler space 42 toward the external refrigerant circuit is effectively attenuated.

(Second Embodiment) In the present embodiment,
It is embodied in the discharge muffler structure of a single-head piston variable displacement compressor. The difference between the compressor and the compressor of the first embodiment is that the discharge capacity can be changed. The refrigerant gas compression mechanism has a similar configuration except that a single-headed piston 59 is used as the piston and the refrigerant gas is sucked, compressed, and discharged only on the rear side of the housings 11, 12, and 14. The corresponding members are given the same numbers and their explanations are omitted.

A configuration for changing the discharge capacity will be described. As shown in FIG. 4, the crank chamber 60 is partitioned between the front housing 12 and the cylinder block 11. The rotary support 61 is fixed to the drive shaft 18 in the crank chamber 60. Swash plate 62
Are supported slidably and tiltably with respect to the drive shaft 18 in the direction of the axis L of the drive shaft 18. The support arm 63 that constitutes the hinge mechanism is provided so as to protrude from the outer peripheral surface of the back surface of the rotary support 61. The guide pin 64, which also constitutes the hinge mechanism, is provided so as to project from the front side of the swash plate 62.
The spherical portion 64 a provided at the tip of each guide pin 64 is connected to the guide hole 63 provided in each support arm 63.
It is slidably inserted in a.

The swash plate 62 is tiltable in the direction of the axis L of the drive shaft 18 and rotatable integrally with the drive shaft 18 by the linkage between the support arm 63 and the guide pin 64. The tilt of the swash plate 62 is caused by the guide hole 63a and the spherical portion 64.
It is guided by the slide guide relationship with a and the slide support action of the drive shaft 18. When the radial center of the swash plate 62 is moved to the cylinder block 11 side, the tilt angle of the swash plate 62 is reduced.

The ring-shaped stopper 65 is provided between the rotary support 61 and the cylinder block 11 so as to drive the drive shaft 1.
It is externally fitted and fixed to 8. The swash plate 62 is the stopper 6
When the swash plate 62 is brought into contact with the swash plate 5, the minimum inclination angle of the swash plate 62 is defined. The tilt angle restricting protrusion 66 is integrally formed on the front surface side of the swash plate 62. The maximum tilt angle of the swash plate 62 is defined by the tilt angle restricting projection 66 contacting the back surface side of the rotary support 61.

The pressure release passage 67 connects the crank chamber 60 and the suction chamber 30. The pressure supply passage 68 is provided in the discharge chamber 33.
And a crank chamber 60 are connected to each other, and a capacity control valve 69 is provided on the passage 68. The pressure-sensitive passage 70 is provided in the suction chamber 3
0 and the same capacity control valve 69 are connected. The same capacity control valve 69 includes a diaphragm 71, and the diaphragm 71 is operated by the pressure level of the suction gas introduced through the pressure sensing passage 70. By the operation of the diaphragm 71,
The valve body 72 adjusts the opening degree of the pressure supply passage 68. As a result, the pressure in the crank chamber 60 is changed, and the difference between the pressure in the crank chamber 60 acting before and after the piston 59 and the pressure in the cylinder bore 21 is adjusted. Therefore, the inclination angle of the swash plate 62 is changed, the stroke of the piston 59 is changed, and the discharge capacity is adjusted. That is, the capacity control valve 69 changes the discharge capacity of the compressor so as to maintain the set suction pressure.

In this embodiment, the front muffler portion 41A is provided in the front housing 12, and the rear muffler portion 41B is provided in the cylinder block 11. Discharge chamber 33 provided only in the rear housing 14
Are communicated with the muffler space 42 via a communication passage 47. The gasket 73 seals the joint surface between the cylinder block 11 and the front housing 12.

As shown in FIGS. 5 and 6, the difference between the gasket 73 and the gasket 51 of the first embodiment is that the two opening regions of the muffler sealing portion 52 defined by the arm portions 53A and 53B. 54a and 54c are closed by partitioning portions 75A and 75B integrally extending from the muffler sealing portion 52 (arm portions 53A and 53B). The inside of the muffler space 42 is partially partitioned by the partition parts 75A and 75B.
Therefore, in the muffler space 42, a passage space 76 in which the communication passage 47 and the discharge port 48 are opened, and the passage space 7
6 and a resonance muffler space 77 communicating with the muffler sealing portion 52 through the opening region 54b. The partition portion 75A is arranged to face the inlet 47a of the communication passage 47.

The discharge gas discharged into the discharge chamber 33 flows into the passage space 76 via the communication passage 47.
A part of the discharge gas that has flowed into the passage space 76 flows in and out of the resonance muffler space 77 through the opening region 54b. The discharge gas in the muffler space 42 is attenuated due to the resonance of the pressure pulsation component as it enters and exits the resonance muffler space 77, and the pressure pulsation of the discharge gas discharged through the discharge port 48 becomes small.

In addition to the same effects as the effects (1) to (3) of the first embodiment, the present embodiment also has the following effects. (1) The muffler space 42 is partially partitioned by the partition parts 75A and 75B. Therefore, the muffler space 4
2 has a complicated internal shape, and in particular, in the present embodiment, the resonance muffler space 77 and the muffler sealing portion 52 which is the neck portion.
A resonator is constituted by the open area 54b of the. As a result, the pressure pulsation of the discharged gas is effectively attenuated.

(2) The muffler sealing part 52 has a partition part 75.
By providing A and 75B, the tensile strength is further increased, and it is more effective in suppressing the above-mentioned deformation. (3) The partition part 75A is arranged to face the inlet 47a of the communication passage 47. Therefore, the discharge gas flowing into the muffler space 42 is directly collided with the partition portion 75A, the flow velocity is weakened, and the damping effect of the pressure pulsation is enhanced.

(4) The partition portions 75A and 75B are integrally formed with the muffler sealing portion 52 (gasket 73).
Therefore, as compared with the case where the opening regions 54a to 54c are sealed with a plate material that is separate from the muffler sealing portion 52,
The number of parts constituting the compressor can be reduced.

It should be noted that, for example, the following embodiments can be carried out without departing from the spirit of the present invention. (1) In the above embodiment, the discharge muffler structure that reduces the pressure pulsation of the discharge gas is embodied, but the present invention is not limited to this, and the suction muffler structure that reduces the pressure pulsation of the intake gas is embodied. You may turn it into. Further, it may be embodied in a structure having both the suction muffler and the discharge muffler. With this configuration, the pressure pulsation of the suction gas can be attenuated, and the vibration and noise caused by the pressure pulsation can be reduced.

(2) In the first embodiment, the front housing 12 and the front cylinder block 11A are provided.
And a muffler space 42 between the rear cylinder block 11B and the rear housing 14.
In this case, the muffler sealing portion 52 is extended from, for example, a gasket included in the front valve forming body 13 (former) or the rear valve forming body 15 (latter).

(3) In the first embodiment, the muffler space 42 is formed so as to extend from the front housing 12 to the rear cylinder block 11B or to extend from the front cylinder block 11A to the rear housing 14. . In this case, the muffler sealing portion 52 is extended from, for example, the gasket 51 and the gaskets included in the valve forming bodies 13 and 15.

(4) In the first embodiment, the muffler space 42 is formed extending from the front housing 12 to the rear housing 14. In this case, the muffler sealing portion 52 is, for example, the gasket 51 and the valve forming bodies 13 and 1.
5 extend from the gaskets respectively.

(5) In the second embodiment, the muffler space 42 is formed between the cylinder block 11 and the rear housing 14. In this case, the muffler sealing portion 52 is extended from, for example, a gasket included in the valve forming body 15.

(6) In the second embodiment, the muffler space 42 is formed extending from the front housing 12 to the rear housing 14. In this case, the muffler sealing unit 5
2 is extended from the gasket provided in the gasket 73 and the valve forming body 15, respectively.

(7) The muffler sealing portion 52 is attached to the gasket 5
Configure separately from 1,73. (8) The partition portions 75A and 75B are configured by a plate material or the like that is separate from the muffler sealing portion 52.

(9) As another piston type compressor, for example, a wave cam type compressor provided with a wave cam instead of a swash plate, and the like, should be embodied in its muffler structure.
By embodying it in the muffler structure of the piston type compressor in which the pressure pulsation of the discharge gas is large, the effect of reducing vibration and noise is effectively exhibited. Note that the muffler structure is not limited to the piston type compressor, and may be embodied in the muffler structure of a rotary type compressor such as a vane type compressor or a scroll type compressor.

The technical idea that can be understood from the above embodiment will be described. (1) The compression mechanism is a cylinder bore 2 formed in cylinder blocks 11A and 11B, which are housing components.
1 and a double-headed piston 22 housed in the cylinder bore 21 and reciprocated, and a discharge gas discharged from a compression chamber 23 formed by being surrounded by the end surface of one piston 22 and the cylinder bore 21. , The other piston 22
The discharge gas discharged from the compression chamber 24 formed by being surrounded by the end surface and the cylinder bore 21 is configured to join in the muffler space 42, and the discharge gas inlet 46a from one compression chamber 23 side. And the other compression chamber 2
The inlet 47a of the gas discharged from the 4 side is the muffler space 42
The muffler structure according to any one of claims 1 to 7, wherein the muffler structure is arranged so that the distance to the outlet 48 of each of them is unequal length.

By doing so, the pressure pulsation of the discharge gas is effectively damped. (2) The muffler structure according to any one of claims 3 to 7, wherein the partition portions 75A, 75B are integrally extended from the muffler sealing gasket 52.

By doing so, the number of parts constituting the compressor can be reduced.

[0058]

According to the invention of claim 1 having the above-mentioned structure, the gasket for the muffler portion is bridged by the arm portion provided so as to traverse the inside of the muffler space, and its tensile strength is enhanced. There is. Further, the through bolt for joining and fixing the housing structure directly penetrates the vicinity of the base portion of the arm portion to directly support the arm portion. Therefore, even if the above-mentioned vibration and the stress caused by the high pressure in the muffler space act on the muffler gasket, the deformation is small, and the deviation from the predetermined sealing position can be suppressed as much as possible. As a result, the predetermined sealing function of the muffler gasket can be maintained.

Further, the refrigerant gas flowing into the muffler space is disturbed by a part of the refrigerant gas colliding with the arm portion, and the damping effect of pressure pulsation is enhanced. According to the invention of claim 2, the plurality of arms are provided, whereby the tensile strength of the muffler gasket is further enhanced. Therefore, the effect of claim 1 is more effectively exhibited.

According to the third aspect of the invention, the inside of the muffler space can be made into a complicated shape by the partition part, and the pressure pulsation of the refrigerant gas can be attenuated more effectively. According to the invention of claim 4, the number of parts of the compressor can be reduced by integrally forming the muffler gasket with the housing gasket.

According to the fifth aspect of the present invention, the refrigerant gas flowing into the muffler space directly collides with the partition section. Therefore, the pressure pulsation of the refrigerant gas is damped more effectively.

According to the sixth aspect of the present invention, the opening region has a muff.
The invention of claim 7 faces the entrance of the space.
According to the above, the discharge gas discharged from one compression chamber
The discharge gas discharged from one of the compression chambers through the opening area
Directly collide with each other. Therefore, the pressure pulse of the discharge gas
Motion is reduced.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a double-headed piston type compressor.

FIG. 2 is a sectional view corresponding to line AA in FIG.

FIG. 3 is a sectional view corresponding to line BB in FIG.

FIG. 4 is a vertical sectional view of a single-head piston variable displacement compressor according to a second embodiment.

5 is a cross-sectional view corresponding to line C-C in FIG.

6 is a cross-sectional view corresponding to line D-D in FIG.

[Explanation of symbols]

11A, 11B ... Cylinder block as a housing structure, 12 ... Similarly front housing, 14 ... Similarly rear housing, 41A, 41B ... Muffler part, 42 ...
Muffler space, 44 ... Second through bolt as through bolt, 52 ... Muffler sealing portion as muffler gasket, 52a ... Inner peripheral edge portion, 53A, 53B ... Arm portion.

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Satoshi Kitahama 2-1-1 Toyota-cho, Kariya city, Aichi, Ltd. Inside Toyota Industries Corporation (56) Reference JP-A-8-114182 (JP, A) 8-35485 (JP, A) Actually open 51-5809 (JP, U) Actually open 60-152077 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F04B 39/00 101 F04B 27/08

Claims (7)

(57) [Claims] 1. A compressor having a structure in which a compression mechanism is housed in a housing in which a plurality of housing constituent members are joined and fixed by through bolts, and a refrigerant gas or the like is sucked in, compressed and discharged by the operation of the compression mechanism. , For the muffler part that forms the muffler space between the muffler parts by providing the muffler parts so that the openings of the adjacent muffler parts face each other, and seals the joint surface of the muffler parts. A muffler structure in which a gasket is provided, the inner peripheral edge portion of the gasket is bridged and connected by an arm portion so as to cross the muffler space, and the through bolt is passed through near the base of the arm portion in the gasket. 2. The muffler structure according to claim 1, wherein the muffler gasket includes a plurality of arms. 3. The muffler structure according to claim 1, wherein the muffler gasket is provided with a partitioning part for partially partitioning the muffler space by closing the opening area defined by the arm part. 4. The muffler structure according to claim 1, wherein the muffler gasket is integrally extended from a housing gasket that seals a joint surface of a housing structure. 5. The muffler structure according to claim 3, wherein the partition portion is provided at a position facing an entrance of the muffler space. 6. An opening area defined by the arm portion.
2. The device according to claim 1, wherein the muffler is provided at a position facing the entrance of the muffler space.
Is the muffler structure described in 2. 7. The compression mechanism includes a cylinder bore formed in a cylinder block, which is a housing structure, and a double-headed piston housed in the cylinder bore and reciprocated, and one piston end surface and the cylinder bore are provided. The discharge gas discharged from the compression chamber formed surrounded by and the discharge gas discharged from the compression chamber formed surrounded by the other piston end surface and the cylinder bore join together in the muffler space. 7. The muffler structure according to claim 6, wherein the inlet of the discharge gas from one compression chamber side and the inlet of the discharge gas from the other compression chamber side are arranged to face each other in the muffler space.