JP2016180352A - Piston type swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a piston type swash plate compressor capable of reducing the shell diameter of a cylinder block.SOLUTION: A cylinder bore 18 is blocked by a partition wall 22 formed integrally with a cylinder block 2. A gasket 4 does not need to seal the cylinder bore 18 but only needs to seal a discharge chamber 28 formed in a cylinder head 6 and a discharge port 26 to each other, and so a bead 43 of the gasket 4 can be arranged on the end face of the partition wall 22 at the further inner periphery side than the outermost periphery position of the cylinder bore 18. This can reduce the shell diameters of the cylinder block 2 and the cylinder head 6 to reduce the weight of the piston type swash plate compressor and improve the mountability thereof on a vehicle.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a piston-type swash plate compressor having an improved gasket mounting structure.

  In the double-headed piston type swash plate compressor disclosed in Patent Document 1, a pair of cylinder blocks are provided at the front and rear, and a swash plate chamber for introducing a refrigerant into a coupling portion is formed. Each cylinder block has its outer ends closed by front and rear housings via a valve plate, a suction valve, a discharge valve and a gasket, respectively. Each housing has a suction chamber on the outside and a discharge chamber on the inside. A drive shaft is supported in a common central shaft hole of each cylinder block. The swash plate fixed to the drive shaft is rotatably accommodated in the swash plate chamber.

  The cylinder block has a plurality of bores arranged in parallel around the drive shaft. In each bore, a double-headed piston moored to a swash plate via a shoe is fitted so as to be freely movable. Each valve plate is formed with a suction hole communicating with the suction chamber of each housing via a suction valve and a gasket between each bore and a discharge valve and retainer integrated gasket between each bore. Discharge holes communicating with the discharge chambers of the respective housings are formed through the. Each cylinder block is formed with a suction passage communicating the swash plate chamber and the suction chamber of each housing, and a discharge passage communicating each discharge chamber of the front and rear housings.

  The gasket is a metal substrate with an elastic film covered on its surface, and includes an outer seal portion that seals the outer shell of the double-headed piston type swash plate compressor, and a high-pressure region and a low-pressure region that are separated in the housing. And an inner seal portion for sealing the gap. Both end edges of the inner seal portion extend in the outer peripheral direction and are connected to the outer seal portion. Curved and raised beads are provided on the outer seal portion and the inner seal portion of the gasket in order to enhance the sealing performance. The bead is crushed and elastically deformed by the sandwiching member, thereby exhibiting sealing properties.

  In the single-head piston swash plate compressor disclosed in Patent Document 2, a front housing is connected to one end surface of a cylinder via a seal ring, and is fastened together with bolts. An annular chamber forming wall having the same diameter as the outer peripheral wall of the cylinder is integrally formed on the other end surface of the cylinder, and a lid is connected to the end surface of the chamber forming wall via a gasket-type seal ring. It is fixed. On the end face side of the cylinder facing the lid, a partition wall for closing the axial end of the cylinder bore is formed integrally with the cylinder.

  A rotary valve provided with a refrigerant introduction passage is integrally formed on a rotating shaft disposed at the center position of the cylinder and the front housing. The partition wall is opposed to the piston across the compression chamber of the cylinder bore and becomes a part of the wall surface forming the compression chamber. A refrigerant discharge port is formed on the partition wall. A discharge chamber is formed between the lid and the cylinder. A valve forming plate and a retainer forming plate are fastened to the partition wall by bolts. The valve forming plate is formed with a discharge valve that is bent and deformed to open and close the discharge port.

  The double-headed piston type swash plate compressor disclosed in Patent Document 2 has a pair of joined cylinders. A plurality of cylinder bores are formed in the cylinder so as to be arranged around the rotation shaft, and a double-headed piston is accommodated in each cylinder. The rear side configuration with respect to the cylinder is the same as that of the single-head piston swash plate compressor. A lid is connected to the front side of the cylinder by a bolt, and a partition wall is integrally formed with the cylinder on the end face side of the cylinder so as to close the cylinder bore. The partition wall becomes a part of the wall surface forming the compression chamber of the cylinder bore and has a refrigerant discharge port. A gasket-type seal ring, a gasket-type valve forming plate having a discharge valve, and a gasket-type retainer forming plate are interposed between the cylinder and the lid.

JP-A-10-169556 JP 2006-83835 A

  In Patent Document 1, a gasket bead that seals a cylinder block, a valve plate, and a housing between the respective members is on the outer peripheral side of the bore in order to seal the bore, the suction hole, the suction chamber, the discharge hole, and the discharge chamber. It must be placed on the outer edge of the cylinder block. For this reason, there is a limit in reducing the cylinder diameter of the cylinder block and the housing.

  Although it is conceivable to reduce the cylinder diameter of the cylinder block by reducing the inner diameter of the bore, it is necessary to increase the overall length of the cylinder block in order to maintain the volume of the bore. For this reason, the bore inner diameter is reduced due to an increase in installation space when the piston-type swash plate compressor is mounted on the vehicle, a lack of strength of the swash plate due to a large inclination of the swash plate during operation of the piston-type swash plate compressor, etc. It causes problems and is not practical.

  Patent Document 2 discloses a piston-type swash plate compressor having a partition wall integrally formed with a cylinder so as to close a cylinder bore. However, a gasket-type seal ring that seals between a cylinder and a lid is disclosed as follows. Similar to Patent Document 1, it is arranged on the outer end face of the cylinder on the outer peripheral side of the cylinder bore. For this reason, it is difficult to reduce the cylinder diameter of the cylinder.

  An object of the present invention is to provide a piston-type swash plate compressor capable of reducing the cylinder diameter of a cylinder block.

  The present invention provides a rotating shaft, a swash plate that can rotate integrally with the rotating shaft, a piston connected to the swash plate, a cylinder block that defines a swash plate chamber that houses the swash plate, and the cylinder block. A cylinder head joined through a gasket and having a discharge chamber formed therein, the cylinder block has a bottomed cylindrical cylinder bore that houses the piston, and the bottom surface of the cylinder bore A discharge port communicating with the discharge chamber is formed, and an annular bead is formed in the gasket in a region sealing the outside of the compressor and the cylinder head, and at least a part of the bead is formed on the rotating shaft. In the radial direction, the cylinder bore is arranged on the inner peripheral side from the outermost peripheral position of the cylinder bore.

  According to claim 1, by disposing at least a part of the bead of the gasket that seals the discharge port and the discharge chamber from the outside of the compressor on the inner peripheral side from the outermost peripheral position of the cylinder block, the position overlaps the cylinder bore. The cylinder diameters of the cylinder block and the cylinder head can be reduced, and the piston type swash plate compressor can be reduced in weight and can be mounted on a vehicle.

  According to a second aspect of the present invention, the bead is disposed on the outer peripheral side of the discharge port. According to the second aspect, since the gasket beads can be disposed as close as possible to the center side of the cylinder block, the cylinder diameters of the cylinder block and the cylinder head can be reduced.

  According to a third aspect of the present invention, the cylinder head is joined to the cylinder block at a position straddling the boundary between the bottom surface and the inner peripheral surface of the cylinder bore. According to claim 3, the pressure generated by the compression process of the refrigerant in the cylinder bore is applied to the boundary between the bottom surface and the inner peripheral surface of the cylinder bore, and this pressure can be received by the cylinder head joined via the bead, This can contribute to securing the strength of the cylinder block.

  According to a fourth aspect of the present invention, a refrigerant suction passage is formed in the rotary shaft, and a lead-out hole that connects the suction passage and the cylinder bore with the rotation of the rotary shaft is formed in the rotary shaft. When the refrigerant suction port is drilled in the partition wall of the cylinder bore, a bead for sealing the suction port must be newly formed in the gasket. However, in claim 4, by forming a lead-out hole in the rotating shaft and forming a rotary valve mechanism for the cylinder bore, there is no need to form a suction port in the partition wall of the cylinder bore, so that a bead for sealing the suction port is eliminated. And the construction of the gasket can be simplified.

  The present invention can reduce the cylinder diameter of the cylinder block in 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 a front view which shows a gasket. It is an expanded sectional view which shows the positional relationship of the bead of a gasket, and a cylinder block. It is an expanded sectional view of a bead of a gasket and a cylinder block compared with a conventional product. It is sectional drawing of a part of gasket in 1st Embodiment. It is an expanded sectional view of a bead of a gasket and a cylinder block which shows a 2nd embodiment. It is a partial sectional view showing other embodiments of a gasket.

(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. A front-side cylinder block 2 and a rear-side cylinder block 3 are sealed members (not shown). Are connected through. A front cylinder head 6 is joined to the front end of the cylinder block 2 with the gasket 4 and the discharge valve 5 interposed therebetween.

  A rear cylinder head 9 is joined to the rear end of the cylinder block 3 with the gasket 7 and the discharge valve 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 valves 5 and 8 are fixed by a plurality of through bolts 10. 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.

The cylinder block 2 is formed by die casting, and five bottomed cylindrical cylinder bores 18 are evenly arranged (see FIG. 2) around the rotation shaft 12 in the cylinder block 2. Similarly, the cylinder block 3 is also formed by die casting, and five bottomed cylindrical cylinder bores 19 are arranged around the rotation shaft 12 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.

  The bottom surface of the cylinder bore 18 formed in the cylinder block 2, the inner peripheral surface, and the end surface of the double-headed piston 20 define a compression chamber 24. That is, the bottom surface of the cylinder bore 18 forms a part of a partition wall 22 between a compression chamber 24 formed in the cylinder block 2 and a discharge chamber 28 (described later) formed in the cylinder head 6. Similarly, the bottom surface, the inner peripheral surface of the cylinder bore 19 formed in the cylinder block 3 and the end surface of the double-headed piston 20 define a compression chamber 25, and the bottom surface of the cylinder bore 19 is a compression chamber formed in the cylinder block 3. 25 and a part of a partition wall 23 formed between a discharge chamber 29 (described later) formed in the cylinder head 9. The partition wall 22 is formed integrally with the cylinder block 2 and closes the front side end portion in the axial direction of the cylinder bore 18. The partition wall 23 is formed integrally with the cylinder block 3 and closes the rear end portion in the axial direction of the cylinder bore 19. A discharge port 26 that penetrates the partition wall 22 is formed in the partition wall 22. A discharge port 27 that penetrates the partition wall 23 is formed in the partition wall 23.

  Although the discharge port 26 is closed by the discharge valve 5, the discharge port 26 is opened when the refrigerant pressure in the compression chamber 24 reaches a certain level or more, and the refrigerant can be discharged into the discharge chamber 28 formed in the cylinder head 6. Similarly, although the discharge port 27 is closed by the discharge valve 8, the discharge port 27 is opened when the refrigerant pressure in the compression chamber 25 exceeds a certain level, and the refrigerant can be discharged into the discharge chamber 29 formed in the cylinder head 9. it can. The discharge chambers 28 and 29 communicate with an external refrigerant circuit (not shown). Further, the opening degree of the discharge valve 5 is regulated by a retainer 30 formed on the gasket 4. The opening degree of the discharge valve 8 is regulated by a retainer 31 formed on the gasket 7.

  At the center of the rotating shaft 12, a refrigerant suction passage 33 is formed in the axial direction of the rotating shaft 12 so as to open the rear end portion and communicate with a suction chamber 32 formed in the cylinder head 9. On the front side of the rotating shaft 12, a refrigerant outlet hole 34 communicating with the suction passage 33 passes through the peripheral wall of the rotating shaft 12 and opens to the peripheral surface. Similarly, on the rear side of the rotating shaft 12, a refrigerant outlet hole 35 communicating with the suction passage 33 passes through the peripheral wall of the rotating shaft 12 and opens on the peripheral surface. The lead-out hole 34 and the lead-out hole 35 communicate with the suction chamber 32 through the suction passage 33. In the cylinder block 2 at a position corresponding to the lead-out hole 34, five introduction holes 36 are formed around the rotation shaft 12 at equal intervals. Each introduction hole 36 communicates with the compression chamber 24 of the cylinder bore 18 formed at five locations of the cylinder block 2.

  Similarly, in the cylinder block 3 at a position corresponding to the lead-out hole 35, five introduction holes 37 are formed at equal intervals around the rotation shaft 12, and each introduction hole 37 is formed in five places in the cylinder block 3. The cylinder bore 19 communicates with the compression chamber 25. Therefore, the lead-out hole 34 and the lead-out hole 35 formed in the rotating shaft 12 constitute a rotary valve mechanism. With the rotation of the rotary shaft 12, the rotary valve mechanism can supply the refrigerant in the suction chamber 32 to the compression chamber 24 at a timing when the outlet hole 34 coincides with the introduction hole 36. Further, the rotary valve mechanism can supply the refrigerant in the suction chamber 32 to the compression chamber 25 at the timing when the lead-out hole 35 coincides with the introduction hole 37 as the rotary shaft 12 rotates.

  The structure of the gasket 4 will be described with reference to FIGS. In addition, since the gasket 4 and the gasket 7 are the same structures, the gasket 4 is demonstrated here and the description of the gasket 4 is used about the gasket 7. FIG. The gasket 4 is formed in a substantially circular shape, and is provided with a shaft hole 38 through which the boss protruding from the front side of the cylinder block 2 passes in the center of the gasket 4 and five bolts 10 (see FIG. 1) through the outer periphery of the gasket 4. Bolt holes 39 are formed. A bulging surface 40 protruding forward is formed around the shaft hole 38 of the gasket 4, and the bulging surface 40 can accommodate the base of the discharge valve 5 (see FIGS. 1 and 3).

  On the outer peripheral side of the bulging surface 40, retainers 30 are formed at five locations at equal intervals. The retainer 30 is formed at a position corresponding to the discharge port 26 of the cylinder bore 18 indicated by an imaginary line, and through holes 41 and 42 are formed on the outer peripheral side and both sides of the retainer 30. The through holes 41 and 42 have a function of circulating the refrigerant in the compression chamber 24 to the discharge chamber 28 (see FIG. 1) when the discharge valve 5 is opened.

  A bead 43 (see FIG. 5) is formed in an annular shape on the outer peripheral edge of the gasket 4 so as to be curved in the radial direction of the gasket 4 in order to improve the sealing performance (in FIG. 2, the ridge line of the bead 43). Is indicated by a thin line). The bead 43 is formed in a region that seals between the outside of the compressor 1 and the cylinder head 6, and is sandwiched between the partition wall 22 and the outer peripheral wall of the cylinder head 6. In the present embodiment, the bead 43 is disposed at a position where the discharge chamber 28 and the bolt hole 39 can be sealed with the outside, but the cylinder bore 18 has a front end portion in the axial direction at the seam with the cylinder block 2. Therefore, it is not necessary to consider the seal at the front side end of the cylinder bore 18.

  Specifically, as shown in FIG. 2, the bead 43 passes through a position on the outer peripheral side of the bolt hole 39 of the gasket 4. Since the cylinder bore 18 is closed at its front end in the axial direction by the partition wall 22, the bead 43 is disposed so as to pass through the position entering the center side of the cylinder bore 18 when the retainer 30 is formed. As shown in FIG. 3, the bead 43 at the position where the retainer 30 is formed is disposed so that the entire bead 43 corresponds to the spatial position of the cylinder bore 18, including the virtual line X <b> 1 in the axial direction passing through the ridgeline of the bead 43. Yes. FIG. 5 is a cross-sectional view of the gasket 4 according to the present embodiment cut in a direction perpendicular to the surface of the gasket 4 and in the radial direction of the rotary shaft 12. As shown in FIG. 5, the bead 43 in the present embodiment is a full bead in which both sides bulge in a slope shape toward the ridge line where the bead 43 is the most bulged portion. It refers to the entire range L1 from the start point to the end of the bulge through the ridgeline.

  In FIG. 4, the inventive product according to the present embodiment and the conventional product are compared and described. In the conventional product, in order to close the cylinder bore 51 by the valve plate 50, a gasket 53 for sealing between the valve plate 50 and the cylinder block 52 and a gasket 55 for sealing between the valve plate 50 and the cylinder head 54 are necessary. .

  The cylinder block 52 has to be thick enough to maintain the strength of the cylinder block 52 and the thickness to dispose the beads 56 of the gasket 53 that seals the cylinder bore 51 so that the cylinder diameter of the cylinder block 52 must be increased. Don't be. The cylinder head 54 is formed with the same cylinder diameter as the cylinder block 52 in order to place the bead 57 of the gasket 55 at the same position as the bead 56 of the gasket 53. Therefore, the imaginary line X2 in the axial direction passing through the ridge lines of the beads 56 and 57 passes through the end face of the cylinder block 52 that is on the outer peripheral side of the cylinder bore 51.

  In the invention, the cylinder bore 18 is closed by a partition wall 22 formed integrally with the cylinder block 2 instead of the conventional valve plate 50. For this reason, the gasket 4 does not need to seal the cylinder bore 18 and only needs to seal the discharge chamber 28 and the discharge port 26 formed in the cylinder head 6. Therefore, the bead 43 of the gasket 4 can be disposed on the end face of the partition wall 22 at a position overlapping the cylinder bore 18.

  In FIG. 4, when viewed in the axial direction of the cylinder bore 18, the virtual line X <b> 1 in the axial direction passing through the ridge line of the bead 43 is disposed so as to overlap the inside of the cylinder bore 18. Specifically, an extension line obtained by extending an imaginary line X <b> 1 passing through the ridge line of the bead 43 in the axial direction of the cylinder bore 18 passes through the inside of the cylinder bore 18. That is, the bead 43 is disposed on the inner peripheral side with respect to the outermost peripheral position 18 </ b> A of the cylinder bore 18 in the radial direction of the rotating shaft 12. As a result, even if the bore diameters of the cylinder bores 18 and 51 of the invention product and the conventional product are the same, the cylinder diameter of the cylinder block 2 can be reduced by the distance D1 in the radial direction from the cylinder diameter of the cylinder block 52 of the conventional product. In addition, the cylinder head 6 has a cylinder diameter that is smaller than the cylinder diameter of the conventional cylinder head 54 by a distance D2 in the radial direction. The cylinder diameter of the cylinder head 6 may be the same as the cylinder diameter of the cylinder block 2, but can be reduced from the cylinder diameter of the cylinder block 2 depending on the position of the bead 43.

  In the first embodiment, the beads 43 of the gasket 4 can be disposed on the end face of the partition wall 22 on the inner peripheral side from the outermost peripheral position of the cylinder bore 18, so that the cylinder diameters of the cylinder block 2 and the cylinder head 6 are reduced. Thus, it is possible to reduce the weight of the double-headed piston type swash plate compressor and to improve the mounting property on the vehicle. Further, since the cylinder bore 18 is closed by the partition wall 22, the gasket 53 shown in the conventional product is not necessary, and the configuration is simplified. Further, by forming the lead-out holes 34 and 35 in the rotating shaft 12 and configuring the rotary valve mechanism for the introduction holes 36 and 37, it is not necessary to form a suction port in the partition wall 22 of the cylinder bore 18, so that The bead for sealing the suction port can be eliminated, and the configuration of the gasket 4 can be simplified.

(Second Embodiment)
FIG. 6 shows the second embodiment. The same components as those in the first embodiment will be described with the same reference numerals, and detailed description thereof will be omitted. In the second embodiment, an imaginary line X <b> 3 in the axial direction passing through the ridge line of the bead 45 formed in the gasket 44 is arranged at a position where it overlaps the inner peripheral surface of the cylinder bore 18.

  The gasket 44 is sandwiched between the end surface of the cylinder block 2 and the end surface of the cylinder head 6. The bead 45 has the same configuration as the bead 43 shown in FIG. 5 and has a range L1. When viewed in the axial direction of the cylinder bore 18, an imaginary line X <b> 3 in the axial direction passing through the ridge line of the bead 45 extends on the inner peripheral surface of the cylinder bore 18. That is, the bead 43 is disposed at a position overlapping the inner peripheral surface of the cylinder bore 18. The half range L1 / 2 on the outer peripheral side from the ridge line of the bead 45 is disposed on the end surface of the cylinder block 2 on the outer peripheral side from the cylinder bore 18, and the half range L1 / 2 on the inner peripheral side from the ridge line of the bead 45 is the cylinder bore. It is arranged on the end face of the partition wall 22 at a position overlapping the 18 internal space. The cylinder head 6 is coupled to the cylinder block 2 such that the outer peripheral wall of the cylinder head 6 sandwiches the bead 43. That is, the outer peripheral wall of the cylinder head 6 is disposed at a position straddling the boundary between the inner peripheral surface and the bottom surface of the cylinder bore 18. A retainer 46 that restricts the opening amount of the discharge valve 5 is formed on the center side of the gasket 44.

  In the second embodiment, a part of the pressure generated in the cylinder bore 18 due to the compression of the refrigerant is received by the bead 45, which can contribute to securing the strength of the cylinder block 2. In the refrigerant compression process, a large pressure is generated in the compression chamber 24 (see FIG. 1) of the cylinder bore 18, and in particular, a large pressure is applied to an edge portion that is a boundary between the inner peripheral surface and the bottom surface of the cylinder bore 18. In the second embodiment, the imaginary line X3 passing through the ridge line of the bead 45 is disposed at a position overlapping the inner peripheral surface of the cylinder bore 18, so that a large pressure generated in the cylinder bore 18 by the cylinder head 6 is received via the gasket 44. This can contribute to securing the strength of the cylinder block 2.

  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) The beads 43, 45 of the gaskets 4, 7, 44 shown in the first and second embodiments can be implemented in the form shown in FIG. FIG. 7 shows a half bead 48 having one side as an inclined surface, and the entire outer peripheral end side of the gasket 47 is bulged so as to be parallel to the center side. The half bead 48 in the gasket 47 indicates a range L <b> 2 from the bulging start position to the bulging end position parallel to the center side of the gasket 47.
(2) In the first and second embodiments, the number of cylinder bores 18 and 19 is not limited to five, and three or more may be disposed around the rotary shaft 12.

(3) In 1st and 2nd embodiment, it can implement not only in a double-headed piston type swash plate type compressor but in a single-headed piston type swash plate type compressor. In the double-headed piston type swash plate compressor and the single-headed piston type swash plate compressor, the first and second embodiments include a fixed capacity type compressor that fixes the swash plate 15 to the rotary shaft 12 or a swash plate 15. The present invention can be implemented in a variable capacity compressor that is movably attached to the rotary shaft 12.
(4) The first and second embodiments can also be implemented in a configuration in which the partition ports 22 and 23 are formed with a suction port communicating with the suction chamber.

1 Double-head piston type swash plate compressor 2, 3 Cylinder blocks 4, 7, 44, 47 Gasket 5, 8 Discharge valve 6, 9 Cylinder head 12 Rotating shaft 15 Swash plate 18, 19 Cylinder bore 18A Outermost peripheral position 20 Double-head piston 22, 23 Partition 24, 25 Compression chamber 26, 27 Discharge port 28, 29 Discharge chamber 30, 31, 46 Retainer 32 Suction chamber 33 Suction passage 34, 35 Lead-out hole 36, 37 Introduction hole 41, 42 Through hole 43, 45 Bead (full bead) )
48 Half bead L1, L2 Bead range X1, X2, X3 Virtual line passing through ridge line of bead

Claims (4)

A rotating shaft, a swash plate that can rotate integrally with the rotating shaft, a piston connected to the swash plate, a cylinder block that defines a swash plate chamber that houses the swash plate, and a cylinder block coupled to each other via a gasket And a cylinder head in which a discharge chamber is formed,
The cylinder block is formed with a bottomed cylindrical cylinder bore that houses the piston, and a bottom surface of the cylinder bore is formed with a discharge port communicating with the discharge chamber,
In the gasket, an annular bead is formed in a region sealing the outside of the compressor and the cylinder head, and at least a part of the bead is located on the inner peripheral side of the outermost peripheral position of the cylinder bore in the radial direction of the rotating shaft. Piston-type swash plate compressor characterized by being arranged in   The piston-type swash plate compressor according to claim 1, wherein the bead is arranged on an outer peripheral side from the discharge port.   2. The piston-type swash plate compressor according to claim 1, wherein the cylinder head is coupled to the cylinder block at a position across a boundary between a bottom surface and an inner peripheral surface of the cylinder bore.   4. A refrigerant suction passage is formed in the rotary shaft, and a lead-out hole for communicating the suction passage and the cylinder bore is formed in the rotary shaft as the rotary shaft rotates. The piston-type swash plate compressor according to any one of the above.

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