JP2015165111A - piston type swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make smooth the flow of refrigerant passing through a throttle hole formed in a gasket and improve the operation efficiency of a piston type swash plate compressor.SOLUTION: Refrigerant discharged from a compression chamber 24 flows into a discharge chamber 53A and is then guided to an inclined surface of a wall surface of a protrusion 65 and smoothly introduced into a communication hole 58. The refrigerant throttled by the communication hole 58 flows into a muffler chamber 47 and expands. Subsequently, the refrigerant is delivered to an external refrigerant circuit from a discharge hole 51 via a discharge passage 48. The discharge pulsation of the refrigerant is, therefore, suppressed by throttling the refrigerant by the communication hole 58 and expansion. Furthermore, the inclined surface of the wall surface of the protrusion 65 can make a flow of the refrigerant smooth, loss in the flow of the refrigerant in the communication hole 58 is reduced, and the operation efficiency of a piston type swash plate compressor 1 is improved. Moreover, high pressure is applied to a gasket 4 when liquid refrigerant is generated at a time of starting; however, stress in response to the pressure is dispersed by the inclined surface of the wall surface and it is possible to prevent the gasket 4 from being deformed and damaged.

Description

  The present invention relates to a piston-type swash plate compressor having a configuration for reducing refrigerant discharge pulsation.

  Patent Document 1 discloses a configuration for suppressing discharge pulsation in a double-headed piston swash plate compressor. In Patent Document 1, the cylinder block is coupled to the head via a valve plate, a discharge valve, and a retainer plate. The cylinder block is formed with a cylinder bore that houses a piston, and the head is formed with a discharge chamber.

  When the double-headed piston type swash plate compressor is operated, the piston reciprocates, and the refrigerant compressed in the cylinder bore is discharged from the compression chamber to the discharge chamber, flows into the discharge passage of the cylinder block, and expands in the discharge passage. Then, after being further squeezed at the port, it flows to the discharge port. Therefore, the discharge pulsation of the refrigerant can be sufficiently reduced by the configuration in which the refrigerant is once squeezed and then expanded in the discharge process.

JP-A-9-287562

  In Patent Document 1, the refrigerant in the discharge chamber is throttled by a port formed in the valve plate in order to reduce discharge pulsation. For this reason, the refrigerant flowing into the discharge passage from the discharge chamber causes a pressure loss, and there is a problem that the operation efficiency of the double-headed piston swash plate compressor is lowered.

  Some double-headed piston type swash plate compressors use a configuration in which a separate valve plate is eliminated and a compression chamber and a discharge chamber are partitioned by a partition wall integrated with a cylinder block. In the double-headed piston swash plate compressor adopting such a configuration, the cylinder block and the head are coupled via a gasket having a retainer. When the double-headed piston swash plate compressor is stopped for a long period of time, the refrigerant gas liquefies and may cause liquid compression at the time of start-up. At that time, the liquid refrigerant is discharged and the liquid refrigerant directed to the communication hole formed in the gasket is Apply high surface pressure to the gasket. For this reason, in the double-headed piston type swash plate compressor, in addition to causing a pressure loss of the refrigerant, a gasket having a lower strength than the valve plate may be deformed or damaged.

  An object of the present invention is to smoothen the flow of refrigerant through a communication hole formed in a gasket and to improve the operation efficiency of a piston-type swash plate compressor.

  The first aspect of the present invention is joined to a rotary shaft, a swash plate that can rotate integrally with the rotary shaft, a cylinder block that defines a swash plate chamber that houses the swash plate, and a gasket sandwiched between ends of the cylinder block, A cylinder head having a discharge chamber formed therein, and the cylinder block has a plurality of cylinder bores formed around the rotation shaft, and a muffler chamber is formed between the cylinder bores. The muffler chamber is partitioned by the gasket while facing each other, and a communication hole is formed in the gasket to connect the discharge chamber and the muffler chamber, so that the discharge refrigerant discharged from the cylinder bore is separated from the discharge chamber. In the piston-type swash plate compressor that circulates between the muffler chamber and the gasket, the gasket is throttled along the flow direction of the discharged refrigerant. Useless protrusion projecting so is formed, and wherein the communicating hole in the projecting portion is formed.

  According to the first aspect, the communication hole of the gasket is formed in the protruding portion, so that the refrigerant can be smoothly flowed while maintaining the refrigerant pulsation suppressing function by the communication hole, and the pressure loss of the refrigerant in the communication hole is reduced. Thus, the operation efficiency of the piston-type swash plate compressor can be increased.

  According to a second aspect of the present invention, the protruding portion projects from the discharge chamber side toward the muffler chamber side. According to the second aspect, the flow resistance of the refrigerant through the communication hole can be reduced. Further, the stress due to the liquid refrigerant at the time of starting the piston-type swash plate compressor can be dispersed by forming the protruding portion, and the gasket can be prevented from being deformed or damaged.

  According to a third aspect of the present invention, the cylinder bore is closed by a partition integral with the cylinder block, the cylinder head is joined to the cylinder block with the gasket and a discharge valve forming plate interposed therebetween, and the opening of the discharge valve is set in the gasket. A restrictor retainer is provided, and the compression chamber of the cylinder bore communicates with the discharge chamber through a discharge port formed in the partition wall and closed by the discharge valve. According to the third aspect of the present invention, in the piston plate swash plate type compressor integrated with the valve plate and cylinder without the separate valve plate, the pressure loss of the refrigerant in the communication hole is reduced, and the operating efficiency of the piston type swash plate type compressor is reduced. Can be increased. Further, high stress generated when the liquid refrigerant is compressed can be dispersed by the formation of the protruding portion, and deformation and damage of the gasket can be prevented.

  According to a fourth aspect of the present invention, the protrusion includes a top surface and a wall surface continuous from the top surface, and the top surface is formed in a circular shape. According to the fourth aspect, the pressure loss of the refrigerant in the communication hole can be reduced, and the operation efficiency of the piston-type swash plate compressor can be increased.

  According to a fifth aspect of the present invention, the projecting portion includes a top surface and a wall surface continuous from the top surface, and the top surface is formed in a square shape. According to the fifth aspect, the pressure loss of the refrigerant in the communication hole can be reduced, and the operation efficiency of the piston-type swash plate compressor can be increased.

  According to a sixth aspect of the present invention, the projecting portion is formed by a projecting portion projecting obliquely toward the muffler chamber side by cutting out a part of the gasket, and a space between the projecting portion and the gasket is formed in the communication hole. It is characterized by that. According to the sixth aspect, the pressure loss of the refrigerant in the communication hole can be reduced, and the operation efficiency of the piston-type swash plate compressor can be increased.

  The present invention can smooth the flow of the refrigerant through the communication hole formed in the gasket, and can improve the operation efficiency of the piston-type swash plate compressor.

It is a longitudinal cross-sectional view of the double-headed piston type swash plate type compressor in 1st Embodiment. It is the sectional view on the AA line of FIG. FIG. 3 is a sectional view taken along line B-B in FIG. 2. It is a rear view of the cylinder head on the front side. (A) is a rear view of a gasket, (b) is the CC sectional view taken on the line of (a). The 2nd Embodiment is shown, (a) is a rear view of a gasket, (b) is the DD sectional view taken on the line of (a). The 3rd Embodiment is shown, (a) is a rear view of a gasket and (b) is an EE line sectional view of (a). It is sectional drawing of the principal part of the valve plate and gasket which shows 4th Embodiment.

(First embodiment)
A first embodiment will be described with reference to FIGS. In this specification, for the sake of convenience, the left side of FIG. FIG. 1 shows a double-headed piston-type swash plate compressor 1 as an example of a piston-type swash plate compressor, in which a front-side cylinder block 2 and a rear-side cylinder block 3 are joined. A front cylinder head 6 is joined to the front end of the cylinder block 2 with a gasket 4 and a discharge valve forming plate 5 interposed therebetween. The rear cylinder head 9 is joined to the rear end of the cylinder block 3 with the gasket 7 and the discharge valve forming plate 8 interposed therebetween. The cylinder blocks 2 and 3 and the cylinder heads 6 and 9 are made of a metal such as aluminum, for example. In addition, the gaskets 4 and 7 are configured, for example, by coating a metal thin plate with an elastic material such as rubber.

  The cylinder blocks 2 and 3, the cylinder heads 6 and 9, the gaskets 4 and 7, and the discharge valve forming plates 5 and 8 are fixed by six through bolts 10 (see FIG. 2). A rotary shaft 12 is inserted into a shaft hole 11 formed through the center of the cylinder blocks 2 and 3 and is rotatably held by the cylinder blocks 2 and 3. A housing chamber 13 formed between the inner peripheral surface of the cylinder head 6 and the rotating shaft 12 houses a lip seal type shaft sealing device 14, and the shaft sealing device 14 supports the front end of the rotating shaft 12. At the same time, the inside of the cylinder head 6 is sealed.

  A swash plate chamber 16 for accommodating a swash plate 15 attached to the rotary shaft 12 so as to be integrally rotatable is formed at the position of the joint between the cylinder blocks 2 and 3. The swash plate 15 is supported by a thrust bearing 17 provided between the cylinder blocks 2 and 3 and the movement of the rotary shaft 12 in the axial direction is restricted.

  In the cylinder block 2, three cylinder bores 18 are evenly arranged around the rotation shaft 12 (see FIG. 2). Similarly, in the cylinder block 3, three cylinder bores 19 are arranged around the rotation shaft 12. They are arranged at equal intervals. The cylinder bores 18 and 19 are arranged on the same axis so as to form a pair and accommodate the double-headed piston 20. The double-headed piston 20 is connected to the swash plate 15 via a pair of shoes 21 at the center. Accordingly, the swash plate 15 that rotates integrally with the rotary shaft 12 reciprocates the double-headed piston 20 in the cylinder bores 18 and 19 in the front-rear direction.

  Partition walls 22 and 23 are formed integrally with the cylinder blocks 2 and 3 at the front end of the cylinder block 2 and the rear end of the cylinder block 3, respectively. The partition walls 22 and 23 close the cylinder bores 18 and 19 and partition the compression chambers 24 and 25 between the two-headed pistons 20. The partition walls 22 and 23 are formed with discharge ports 26 and 27 penetrating the partition walls 22 and 23. The discharge ports 26 and 27 are closed by discharge valves 28 and 29 formed on the discharge valve forming plates 5 and 8, but are opened when the refrigerant pressure in the compression chambers 24 and 25 exceeds a certain level, and discharges the refrigerant. can do. Further, the opening degree of the discharge valves 28 and 29 is regulated by retainers 30 and 31 formed in the gaskets 4 and 7.

  Further, as shown in FIGS. 1 and 2, the cylinder block 2 is provided with three suction chambers 32 around the rotating shaft 12. The suction chamber 32 is formed between two adjacent cylinder bores 18 and is arranged at equal intervals in the circumferential direction of the rotary shaft 12. Similarly, in the cylinder block 3, three suction chambers 33 are arranged around the rotation shaft 12 in the same phase as the suction chamber 32. One of the suction chambers 32 and 33 communicates with the suction hole 36 through suction passages 34 and 35 formed in the cylinder blocks 2 and 3, respectively. The suction hole 36 is formed in the outer peripheral portion of the cylinder block 2 and is connected to an external refrigerant circuit (not shown).

  On the other hand, the three suction chambers 32 of the cylinder block 2 are respectively provided with refrigerant supply holes 37 that open to the shaft hole 11 of the rotating shaft 12, and the three cylinder bores 18 each of the refrigerant that opens to the shaft hole 11. An introduction hole 38 is provided. A part of the circumferential surface of the rotary shaft 12 is notched in the rotary shaft 12, and an introduction groove 39 is formed. The introduction groove 39 has a notch length in the circumferential direction of the rotary shaft 12 so that the supply hole 37 of one suction chamber 32 and the introduction hole 38 of one cylinder bore 18 can communicate with each other simultaneously. When the rotary shaft 12 rotates, the introduction groove 39 can sequentially switch the communication state between the supply hole 37 and the introduction hole 38 and sequentially supply the refrigerant in the suction chamber 32 to the three cylinder bores 18. Therefore, the introduction groove 39 of the rotating shaft 12 has a function of a rotary valve for supplying refrigerant.

  The three suction chambers 32 are communicated with three suction chambers 40 formed in the front cylinder head 6 through through holes 41 formed in the gasket 4 and the discharge valve forming plate 5. The three suction chambers 40 communicate with each other via the storage chamber 13 that stores the shaft seal device 14. Accordingly, the refrigerant sucked into one suction chamber 32 communicating with the suction hole 36 is also filled into the other two suction chambers 32 via the storage chamber 13.

  The three suction chambers 33 formed in the cylinder block 3 are each constituted by three suction chambers 42 formed in the cylinder head 9 on the rear side, and through holes 43 formed in the gasket 7 and the discharge valve forming plate 8. It is communicated. Each suction chamber 42 communicates with a common suction chamber 44 formed at the center of the cylinder head 9. An introduction groove 45 formed by cutting out a part of the peripheral surface of the rotation shaft 12 is provided at the rear end portion of the rotation shaft 12. The introduction groove 45 is always in communication with the suction chamber 44 at the rear end. The three cylinder bores 19 are formed with introduction holes 46 that open to the shaft hole 11. Therefore, as the rotary shaft 12 rotates, the introduction groove 45 functions as a rotary valve and can sequentially communicate with the introduction holes 46 of the three cylinder bores 19 to supply the refrigerant in the suction chamber 44.

  As shown in FIGS. 2 and 3, the cylinder block 2 is formed with a muffler chamber 47 as a refrigerant discharge space and a discharge passage 48 communicating with the muffler chamber 47 at a position on the outer peripheral side of the suction chamber 32. Has been. Similarly, in the cylinder block 3, a muffler chamber 49 serving as a refrigerant discharge space and a discharge passage 50 communicating with the muffler chamber 49 are formed at a position on the outer peripheral side of the suction chamber 33. The discharge passages 48 and 50 open to the outer peripheral surface of the cylinder block 2 and communicate with a discharge hole 51 connected to an external refrigerant circuit (not shown).

  As shown in FIGS. 3 and 4, three discharge chambers 52 </ b> A, 52 </ b> B, and 52 </ b> C are formed in the front-side cylinder head 6 at positions facing the three cylinder bores 18. A discharge chamber 53A is formed between the discharge chambers 52B and 52C at a position on the outer peripheral side of the suction chamber 40, and a discharge chamber 53A is formed between the discharge chambers 52A and 52B at a position on the outer peripheral side of the suction chamber 40. A chamber 53B is formed. The discharge chamber 53 </ b> A is provided at a position facing the muffler chamber 47 of the cylinder block 2 through the gasket 4. Since the gasket 4 is configured to partition the discharge chamber 53A and the muffler chamber 47 without using a partition wall such as a valve plate, the gasket 4 is relatively easily deformed by a large pressure.

  The discharge chamber 52A communicates with the discharge chamber 53B through the communication passage 54, the discharge chamber 53B communicates with the discharge chamber 52B through the communication passage 55, and the discharge chamber 52B and the discharge chamber 52C through the communication passages 56 and 57, respectively. And communicated with the discharge chamber 53A. The discharge chamber 53 A is partitioned from the muffler chamber 47 by the gasket 4, and the discharge chamber 53 B is sealed by the gasket 4. One discharge chamber 53 </ b> A and the muffler chamber 47 on the cylinder head 6 side are communicated with each other through a communication hole 58 formed in the gasket 4. The gasket 4 has a function of sealing the compression chamber 24 with the suction chamber 40 and the discharge chambers 52A, 52B, 52C, 53A, 53B.

  Accordingly, the discharge chambers 52A, 52B, 52C, 53A, 53B communicated by the communication passages 54, 55, 56, 57 form the discharge space of the cylinder head 6 and constitute the discharge chamber as a whole. The structure of the discharge chamber 52A, 52B, 52C, 53A, 53B formed in the cylinder head 6 and the communication hole 58 formed in the gasket 4 and the communication passages 54, 55, 56, 57 is the rear cylinder head. 9 is formed in the same manner. 1 and 3, only the discharge chambers 59A, 59C, 60A, 60B formed in positions with different phases and the communication hole 61 formed in the gasket 7 are shown as the discharge chamber of the cylinder head 9 on the rear side. Yes.

  Here, the structure of the communication hole 58 formed in the gasket 4 will be described in detail below. Since the communication hole 61 formed in the gasket 7 is configured in the same way as the communication hole 58, detailed description thereof is omitted. As shown in FIG. 5 (a), the gasket 4 has a hole 62 through which the rotary shaft 12 passes, and three through holes 41 that are arranged uniformly around the hole 62 and communicate with the suction chambers 32, 40. The three retainers 30 disposed between the through holes 41 on the outer peripheral side, the communication holes 58 formed on the outer peripheral side of the through holes 41 and the communication holes 58 communicating with the muffler chamber 47 and the retainer 30 are formed. Holes 63 through which the six through bolts 10 are formed are formed.

  The retainer 30 has a form projecting obliquely into the discharge chambers 52 </ b> A, 52 </ b> B, 52 </ b> C (see FIGS. 1 and 3), and an arc-shaped refrigerant passage 64 is formed between the retainer 30 and the gasket 4. The gasket 4 is formed with a protruding portion 65 that projects so as to be narrowed along the flow direction of the discharged refrigerant from the discharge chamber 53A side to the muffler chamber 47 side. The protruding portion 65 projects in a circular shape so as to reduce the diameter toward the muffler chamber 47 side, and extends from the top surface of the protruding portion 65 located on the muffler chamber 47 side toward the discharge chamber 53A. And a wall surface 66. As shown in FIG. 5B, the communication hole 58 is formed at the center of the top surface of the protrusion 65. The wall surface 66 located on the discharge chamber 53 </ b> A side is formed by an inclined surface extending toward the communication hole 58. Therefore, the inclined wall surface 66 can introduce the refrigerant in the discharge chamber 53A into the communication hole 58 in a smooth flow along the inclined surface.

  The double-headed piston swash plate compressor 1 in the first embodiment can flow the refrigerant as follows. The refrigerant sucked from the suction hole 36 is introduced into the suction chambers 32 and 33 through the suction passages 34 and 35. The refrigerant filled in the suction chamber 32 of the cylinder block 2 fills the other two suction chambers 32 from the suction chamber 40 formed in the front cylinder head 6 via the storage chamber 13. As the rotary shaft 12 rotates, the introduction groove 39 sequentially connects the supply hole 37 and the introduction hole 38 and supplies the refrigerant to the compression chamber 24 of any of the three cylinder bores 18.

  The refrigerant filled in the suction chamber 33 of the cylinder block 3 is supplied to the common suction chamber 44 from the suction chamber 42 formed in the cylinder head 9 on the rear side, and the other two suction chambers 33 through the other suction chambers 42. To fill in. Along with the rotation of the rotating shaft 12, the introduction groove 45 sequentially connects the suction chamber 44 and the introduction hole 46 and supplies the refrigerant to the compression chamber 25 of any of the three cylinder bores 19.

  Next, the flow of the refrigerant will be described taking the cylinder bore 18 shown in FIG. 3 as an example. When the double-headed piston 20 moves to the front side, the refrigerant introduced into the compression chamber 24 is compressed. The compressed refrigerant opens the discharge valve 28 and is discharged from the discharge port 26 to the discharge chamber 52A. As shown in FIG. 4, the refrigerant in the discharge chamber 52 </ b> A is throttled in the communication passage 54 and then flows into the discharge chamber 53 </ b> B to expand. The refrigerant flowing into the discharge chamber 53B is squeezed again by the communication passage 55 and then flows into the adjacent discharge chamber 52B to expand. The refrigerant flowing into the discharge chamber 52B is further throttled by the communication passage 56 and then flows into the discharge chamber 53A to expand.

  The refrigerant discharged from the compression chamber 24 to the discharge chamber 52B is squeezed by the communication path 56 and then directly flows into the discharge chamber 53A to expand. Further, the refrigerant discharged from the compression chamber 24 to the discharge chamber 52C is squeezed by the communication passage 57 and then directly flows into the discharge chamber 53A to expand. The refrigerant that has flowed into the discharge chamber 53 </ b> A is guided by the inclined surface of the wall surface 66 of the protrusion 65 and is smoothly introduced into the communication hole 58. The refrigerant squeezed by the communication hole 58 flows into the muffler chamber 47 and expands. Further, the refrigerant flowing into the muffler chamber 47 flows through the discharge passage 48 and is led out from the discharge hole 51 to the external refrigerant circuit.

  Therefore, the discharge pulsation of the refrigerant discharged from the compression chamber 24 is suppressed by multiple throttling and expansion by the communication passages 54 to 57 and the communication hole 58. Further, the inclined surface of the wall surface 66 of the protruding portion 65 facilitates the circulation of the refrigerant, reduces the pressure loss of the refrigerant in the communication hole 58, and can increase the operating efficiency of the double-headed piston swash plate compressor 1. . Further, when the double-headed piston swash plate compressor 1 is stopped for a long period of time, the refrigerant may be liquefied and the liquid refrigerant may accumulate in the double-headed piston swash plate compressor 1. When the double-headed piston swash plate compressor 1 is started in a state where the liquid refrigerant is accumulated, a high pressure is applied to the gasket 4. In the double-headed piston swash plate compressor 1 of the present embodiment, the opposed discharge chambers 53A, 60A and the muffler chambers 47, 49 are partitioned by only the gaskets 4, 7 without a partition wall (valve plate). The stress caused by the liquid refrigerant is dispersed by the top surface of the protrusion 65 and the inclined surface of the wall surface 66, so that the gaskets 4 and 7 are prevented from being deformed or damaged. The same effect is also produced in the refrigerant discharged from the other cylinder bores 19 on the front side and the rear side.

(Second Embodiment)
FIG. 6 shows the second embodiment. The same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. 2nd Embodiment changes the structure of the protrusion part 65 and the communicating holes 58 and 61 in 1st Embodiment. As shown in FIG. 6A, the projecting portion 67 is formed in a quadrangular shape and projects so as to be reduced in diameter toward the muffler chamber 47 side. Two communication holes 68 and 69 formed in a long hole are provided on the top surface of the protruding portion 67, and a wall surface 70 that is continuous from the top surface to the discharge chamber 53A side is provided. Further, as shown in FIG. 6B, the four surfaces of the wall surface 70 of the protrusion 67 located on the discharge chamber 53A side are formed as inclined surfaces extending toward the communication holes 68 and 69. Accordingly, the refrigerant in the discharge chamber 53 </ b> A is smoothly guided by the inclined surface of the wall surface 70 and introduced into the communication holes 68 and 69. The communication holes 68 and 69 are not limited to the long holes, and may be configured to have a plurality of circular holes. The protrusion 65 in the second embodiment can obtain the same effects as those in the first embodiment.

(Third embodiment)
FIG. 7 shows the third embodiment. The same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. In the third embodiment, the configuration of the protruding portion 65 and the communication holes 58 and 61 in the first embodiment is changed. As shown in FIG. 7A, the projecting portion 71 has a configuration similar to that of the retainer 30, and a part of the gasket 4 is cut out in an arc shape in the circumferential direction of the gasket 4 so as to be inclined toward the muffler chamber 47 side. It is formed by overhanging. A step is formed between the notch portion of the projecting portion 71 and the gasket 4 to create a space. Therefore, the space of the step portion is configured as an arc-shaped communication hole 72. Further, as shown in FIG. 7B, the wall surface 73 located on the discharge chamber 53 </ b> A side of the protrusion 71 is formed as an inclined surface extending toward the communication hole 72. Therefore, the refrigerant in the discharge chamber 53 </ b> A is smoothly guided by the inclined surface of the wall surface 73 and introduced into the communication hole 72. The protrusion 71 in the third embodiment can obtain the same effects as those in the first embodiment.

(Fourth embodiment)
FIG. 8 shows the fourth embodiment. The same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. In the fourth embodiment, the cylinder bores 18 and 19 and the discharge chambers 52A and 59A shown in FIG. 3 are partitioned by the partition walls 22 and 23 integrated with the cylinder blocks 2 and 3 as in the first embodiment. Instead of this, the valve plate 74 and the gasket 75 are separated from each other. In the gasket 75 according to the fourth embodiment, a protrusion 77 having the same configuration as that of the first embodiment is formed.

  The projecting portion 77 is formed so as to project toward the muffler chamber 47, and a communication hole 78 is formed in the projecting portion of the projecting portion 77. The wall surface 79 located on the discharge chamber 53 </ b> A side of the protruding portion 77 is formed as an inclined surface extending toward the communication hole 78. The valve plate 74 is formed with an opening 80 including the entire wall surface 79 of the protrusion 77. Therefore, after passing through the opening 80, the refrigerant in the discharge chamber 53 </ b> A is smoothly guided by the inclined surface of the wall surface 79 of the protrusion 77 and introduced into the communication hole 78. The protrusion 77 in the third embodiment can obtain the same effects as those in the first embodiment.

  The present invention is not limited to the configuration of each of the embodiments described above, and various modifications are possible within the scope of the gist of the present invention, and can be implemented as follows.

(1) In the first to fourth embodiments, the communication holes 58, 61, 68, 69, 72, and 78 are not limited to round holes and long holes, but are formed in various shapes such as elliptical holes and square holes. One or a plurality of them can be formed.
(2) The protruding amounts of the protrusions 65, 67, 71 and 77 in the first to fourth embodiments can be variously changed according to the flow of the refrigerant, and the resonance frequency of the muffler chambers 47 and 49 can be changed. it can. Further, the inclined surfaces of the wall surfaces 66, 70, 73 and 79 can be set at various angles according to the flow velocity or pressure of the refrigerant.
(3) As shown in the first to fourth embodiments, the projecting portions 65, 67, 71, 77 are not limited to the configuration of projecting from the discharge chamber 53A, 60A side toward the muffler chamber 47, 49 side, When the cylinder heads 6 and 9 are provided with a plurality of discharge spaces that are not in direct communication with each other, the cylinder heads 6 and 9 may be configured to project from the muffler chambers 47 and 49 toward the discharge space.
(4) 1st-4th embodiment can be implemented not only in a double-headed piston type swash plate type compressor but in a single-headed piston type swash plate type compressor.

1 Double-head piston type swash plate compressor 2, 3 Cylinder block 4, 75 Gasket 6, 9 Cylinder head 18, 19 Cylinder bore 22, 23 Bulkhead 24, 25 Compression chamber 47, 49 Muffler chamber 48, 50 Discharge passage 51 Discharge hole 52A, 52B, 52C, 59A, 59C, 53A, 53B, 60A, 60B Discharge chamber 54-57 Communication path 58, 61, 68, 69, 72, 78 Communication hole 65, 67, 71, 77 Protrusion 66, 70, 73, 79 Wall 74 Valve plate

Claims (6)

A discharge shaft is formed by joining a rotation shaft, a swash plate that can rotate integrally with the rotation shaft, a cylinder block that defines a swash plate chamber that houses the swash plate, and a gasket sandwiched between ends of the cylinder block. The cylinder block has a plurality of cylinder bores formed around the rotating shaft, and a muffler chamber is formed between the cylinder bores, and the discharge chamber and the muffler chamber are connected to each other. The gasket is partitioned by the gasket while being opposed to each other, and a communication hole is formed in the gasket to communicate the discharge chamber and the muffler chamber, so that the refrigerant discharged from the cylinder bore can be discharged between the discharge chamber and the muffler chamber. In the piston-type swash plate compressor that circulates between
The piston-type swash plate compressor, wherein the gasket is formed with a projecting portion extending so as to be narrowed along a flow direction of the discharged refrigerant, and the communication hole is formed in the projecting portion.   2. The piston-type swash plate compressor according to claim 1, wherein the protruding portion projects from the discharge chamber side toward the muffler chamber side.   The cylinder bore is closed by a partition wall integrated with the cylinder block, the cylinder head is joined to the cylinder block with the gasket and a discharge valve forming plate in between, and a retainer for restricting the opening of the discharge valve is provided on the gasket. 3. The piston type according to claim 1, wherein the compression chamber of the cylinder bore communicates with the discharge chamber through a discharge port formed in the partition and closed by the discharge valve. Swash plate compressor.   The piston according to any one of claims 1 to 3, wherein the projecting portion includes a top surface and a wall surface continuous from the top surface, and the top surface is formed in a circular shape. Type swash plate compressor.   The piston according to any one of claims 1 to 3, wherein the protruding portion includes a top surface and a wall surface continuous from the top surface, and the top surface is formed in a square shape. Type swash plate compressor.   The projecting portion is formed by a projecting portion projecting obliquely toward the muffler chamber side by cutting out a part of the gasket, and a space between the projecting portion and the gasket is used as the communication hole. The piston-type swash plate compressor according to any one of claims 1 to 3.

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