JP4929112B2 - Swash plate compressor - Google Patents

Description

  The present invention relates to a swash plate type compressor capable of changing a discharge capacity used in, for example, a vehicle air conditioner.

  In recent years, various developments have been made on swash plate compressors, and a prior art of a swash plate compressor is disclosed in Patent Document 1.

  In other words, the swash plate compressor according to the prior art compresses refrigerant gas (an example of gas) and includes a housing, and the housing has a cylinder bore therein. Further, the housing has a crank chamber on the front side of the cylinder bore in the interior, and has a suction chamber and a discharge chamber in communication with the cylinder bore on the rear side of the cylinder bore in the interior.

  A drive shaft extending in the front-rear direction is rotatably provided in the housing, and a front end portion of the drive shaft is interlocked and connected to an engine (an example of an external drive source) via a clutch. A single-headed piston is provided in the cylinder bore so as to be able to reciprocate. The piston has a pair of shoes on the head. Further, a lug plate is integrally provided on the drive shaft, and this lug plate is located in the crank chamber.

  A swash plate is provided on the rear side of the lug plate on the drive shaft so as to be tiltable, and this swash plate is located in the crank chamber. The swash plate is connected to the lug plate, and the peripheral portion of the swash plate is engaged with a pair of shoes in the piston so as to be slidable. Further, a stopper for restricting the oblique angle of the swash plate is formed on the front surface of the swash plate, and this stopper can contact the rear surface of the lug plate. A guide hole is formed from the stopper to the swash plate to guide oil mist from the inner surface of the stopper toward the periphery of the swash plate.

  Therefore, by rotating the drive shaft by driving the engine, the lug plate and the swash plate are rotated, and the piston is reciprocated under a stroke corresponding to the oblique angle of the swash plate. Thereby, the refrigerant gas sucked from the suction chamber can be compressed in the cylinder bore, and the compressed refrigerant gas can be discharged from the cylinder bore to the discharge chamber. As is well known, during operation of the swash plate compressor, the crank chamber is filled with oil mist due to scattering of lubricating oil stored in the crank chamber.

  Here, during operation of the swash plate compressor, by adjusting the differential pressure between the pressure on the front side of the piston (crank chamber pressure) and the pressure on the rear side of the piston (cylinder bore chamber pressure), the swash plate angle is increased. Thus, the stroke of the piston can be increased, or the bevel angle of the swash plate can be decreased to reduce the stroke of the piston. Thereby, the discharge capacity of the refrigerant gas can be varied during the operation of the swash plate compressor.

In addition, during operation of the swash plate compressor, a part of the oil mist near the drive shaft flows along the inner surface of the stopper to the inlet of the guide hole, and from the inner surface of the stopper to the periphery of the swash plate by the guide hole. Is directed towards. Thereby, lubrication between the shoe and the peripheral portion of the swash plate in the piston can be performed, and wear of the shoe and swash plate in the piston can be suppressed.
JP 2001-153037 A

  By the way, many oil mists flowing along the inner surface of the stopper do not flow into the guide hole but scatter from the stopper, and the lubrication efficiency between the shoe and the periphery of the swash plate in the piston Will fall. For this reason, the wear of the shoe and the swash plate in the piston cannot be sufficiently suppressed, and there is a problem that it is difficult to improve the durability of the swash plate compressor.

  Accordingly, an object of the present invention is to provide a swash plate compressor having a novel configuration capable of solving the above-described problems.

  A first feature of the present invention (feature of the invention described in claim 1) is a swash plate compressor that compresses gas, and has a cylinder bore inside, and a crank chamber on the front side of the cylinder bore inside, A housing having a suction chamber and a discharge chamber communicating with the inside of the cylinder bore on the rear side of the cylinder bore in the interior, a drive shaft rotatably provided in the housing and extending in the front-rear direction, and reciprocating in the cylinder bore A single-headed piston having a pair of shoes on the head, a lug plate provided integrally with the drive shaft and positioned in the crank chamber, and a rear of the lug plate on the drive shaft; A slant that is tiltable to the side, is located in the crank chamber, is connected to the lug plate, and has a peripheral portion that is slidably engaged with the pair of shoes in the piston. And a stopper provided on the front surface of the swash plate and capable of contacting the rear surface of the lug plate and restricting the oblique angle of the swash plate, and the inner side surface of the stopper has the drive shaft The inner surface of the stopper has a curved shape so that the distance gradually changes from the axial center of the stopper to the front passage formation region that is always farthest from the axial center of the drive shaft among the entire inner surface of the stopper. The gist is that a front guide passage for guiding oil mist from the side surface toward the periphery of the swash plate is formed.

  In the claims and the specification of the present application, “provided” means that it is indirectly provided via a separate member, and that it is formed.

  According to the first feature, by rotating the drive shaft, the lug plate and the swash plate are rotated, and the piston is reciprocated under a stroke corresponding to the oblique angle of the swash plate. Thereby, the gas sucked from the suction chamber can be compressed in the cylinder bore, and the compressed gas can be discharged from the cylinder bore to the discharge chamber. As is well known, during operation of the swash plate compressor, the crank chamber is filled with oil mist due to scattering of lubricating oil stored in the crank chamber.

  Further, during the operation of the swash plate compressor, the swash plate slant is adjusted by adjusting the differential pressure between the pressure on the front side of the piston (crank chamber pressure) and the pressure on the rear side of the piston (cylinder bore chamber pressure). The angle can be increased to increase the piston stroke, or the swash plate can be decreased to reduce the piston stroke. As a result, the gas discharge capacity can be varied during operation of the swash plate compressor.

  Further, during the operation of the swash plate compressor, a part of the oil mist near the drive shaft flows to the entrance of the front guide passage along the inner side surface of the stopper, and the stopper guide It is guided from the inner surface toward the periphery of the swash plate.

  Here, the inner side surface of the stopper has a curved shape such that the distance gradually changes from the axis of the drive shaft, and the entire inner surface of the stopper is always from the axis of the drive shaft. Since the front guide passage is formed in the farthest front passage formation region, the oil mist flowing along the inner surface of the stopper can be easily flowed into the front guide passage by the action of centrifugal force. Thereby, the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be increased.

  The second feature of the present invention (the feature of the invention described in claim 2) is that, in addition to the first feature, the entrance of the front guide passage is when the stopper is brought into contact with the rear surface of the lug plate. Further, the gist of the invention is that it is further away from the axis of the drive shaft than the tip of the stopper.

  According to the second feature, when the stopper is brought into contact with the rear surface of the lug plate, the entrance of the front guide passage is further away from the axis of the drive shaft than the tip of the stopper. Therefore, oil mist can be prevented from leaking from the tip of the stopper, and the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be further increased.

  According to a third feature of the present invention (a feature of the invention described in claim 3), in addition to the first feature or the second feature, the inner surface of the stopper has a plurality of the front passage forming regions. The gist of the invention is that the front guide passages are formed in a plurality of front passage formation regions on the inner surface of the stopper.

  According to the third feature, since the front guide passages are formed in the plurality of front passage formation regions on the inner side surface of the stopper, a wide range from the inner side surface of the stopper toward the front surface of the peripheral portion of the swash plate. Oil mist can be supplied to the piston, and the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be further increased.

  According to a fourth feature of the present invention (a feature of the invention described in claim 4), in addition to the feature of either the first feature or the second feature, the outlet of the front guide passage is the diagonal. The gist of the present invention is that it is close to the front high-load region that is most forwardly offset when the stopper is brought into contact with the rear surface of the lug plate, in the entire front surface region of the peripheral portion of the plate.

  Here, the front high load region is a region that receives a high load from the piston during gas suction.

  According to a fourth feature, since the outlet of the front guide passage is close to the front high load area on the front surface of the peripheral portion of the swash plate, the peripheral portion of the swash plate extends from the inner surface of the stopper. Oil mist can be intensively supplied to the front high load region on the front surface of the piston, and the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be further increased.

  A fifth feature of the present invention (a feature of the invention described in claim 5) is that, in addition to the first feature to the fourth feature, the inner surface of the stopper has an elliptic arc shape. To do.

  A sixth feature of the present invention (a feature of the invention described in claim 6) includes, in addition to the first feature to the fifth feature, an annular protrusion provided on the rear surface of the swash plate, The inner surface of the protrusion has a curved shape so that the distance gradually changes from the axis of the drive shaft, and the rear surface that is always farthest from the axis of the drive shaft in the entire inner surface area of the protrusion. The gist is that a rear guide passage for guiding oil mist from the inner side surface of the protrusion toward the periphery of the swash plate is formed in the passage formation region.

  According to the sixth feature, during the operation of the swash plate compressor, a part of the oil mist near the drive shaft is moved from the inner side surface of the stopper to the peripheral portion of the swash plate by the front guide passage. In addition to being guided, it flows along the inner surface of the protrusion to the entrance of the rear guide passage, and is guided from the inner surface of the protrusion toward the periphery of the swash plate by the rear guide passage.

  Here, the inner surface of the protrusion has a curved shape such that the distance gradually changes from the axis of the drive shaft, and the entire inner surface of the protrusion always has the axis of the drive shaft. Since the rear guide passage is formed in the rear passage formation region farthest away, oil mist flowing along the inner surface of the protrusion can be easily flowed into the rear guide passage by the action of centrifugal force. Thereby, the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be further increased.

  According to a seventh feature of the present invention (a feature of the invention described in claim 7), in addition to the sixth feature, an inner surface of the projection has a plurality of the rear passage forming regions, and the projection The gist of the present invention is that the rear guide passages are respectively formed in a plurality of the rear passage formation regions on the inner side surface.

  According to the seventh feature, since the rear guide passage is formed in a plurality of the rear passage formation regions on the inner side surface of the projection, a wide range from the inner side surface of the projection toward the rear surface of the peripheral portion of the swash plate. Oil mist can be supplied to the piston, and the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be further enhanced.

  The eighth feature of the present invention (the feature of the invention described in claim 8) is that, in addition to the sixth feature, the outlet of the rear guide passage is the total area of the rear surface of the peripheral portion of the swash plate. The gist is that when the stopper is brought into contact with the rear surface of the lug plate, it comes close to the rear high load region that is most rearwardly offset.

  Here, the rear high load region is a region that receives a high load from the piston during gas compression.

  According to an eighth feature, since the exit of the rear guide passage is close to the rear high load region on the rear surface of the peripheral portion of the swash plate, the peripheral portion of the swash plate is formed from the inner surface of the protrusion. Oil mist can be intensively supplied to the rear high load region on the rear surface, and the lubrication efficiency between the shoe and the peripheral portion of the swash plate in the piston can be further enhanced.

  The ninth feature of the present invention (the feature of the invention described in claim 9) is that, in addition to the sixth feature to the eighth feature, the inner surface of the protrusion has an elliptic arc shape. To do.

  According to the first to ninth aspects of the invention, since the lubrication efficiency between the shoe in the piston and the peripheral portion of the swash plate can be increased, the shoe and the swash plate in the piston are worn. Is sufficiently suppressed, and the durability of the swash plate compressor can be improved.

  An embodiment of the present invention will be described with reference to FIGS.

  Here, FIGS. 1 and 2 are side sectional views of the swash plate compressor according to the embodiment of the present invention, and FIG. 3A is a perspective view showing a front side portion of the swash plate on which stoppers and protrusions are formed, 3B is a perspective view showing a rear side portion of the swash plate on which the stopper and the protrusion are formed, FIG. 4A is a front view of the swash plate on which the stopper and the protrusion are formed, and FIG. 4B. Fig. 5 is a side sectional view of a swash plate on which stoppers and projections are formed. Fig. 5 is a front view of another embodiment of the swash plate on which stoppers and projections are formed. Fig. 6 is a diagram of a swash plate on which stoppers and projections are formed. It is a rear view. In the figure, “F” indicates the forward direction, and “R” indicates the backward direction.

  As shown in FIGS. 1 and 2, a swash plate compressor 1 according to an embodiment of the present invention is used in a vehicle air conditioner and includes a housing 3. The housing 3 includes a front housing 5, a rear housing 9 provided by a plurality of mounting bolts 7 (only one is shown) on the rear side of the front housing 5, and a front housing 5 on the front side of the rear housing 9. A cylinder block 15 provided with a plurality of (only one shown) mounting bolts 13 are provided via the valve plate 11 in the accommodated state.

  In the cylinder block 15, a plurality of cylinder bores 17 are formed along the circumferential direction. In other words, the housing 3 has a plurality of cylinder bores 17 inside. The front housing 5 has a crank chamber 19 inside. In other words, the housing 3 has a crank chamber 19 on the front side of the cylinder bore 17 inside. Further, the rear housing 9 has a suction chamber 21 and a discharge chamber 23 communicating with the plurality of cylinder bores 17. In other words, the housing 3 is disposed on the rear side of the cylinder bore 17 inside the suction chamber 21 and the discharge chamber 23. A discharge chamber 23 is provided. The suction chamber 21 is disposed so as to surround the discharge chamber 23, and the suction chamber 21 and the discharge chamber 23 are connected to an external refrigerant circuit (not shown).

  The valve plate 11 is formed with a plurality of suction holes (not shown) communicating with the plurality of cylinder bores 17 and the suction chamber 21, and in one direction from the suction chamber 21 to the cylinder bore 17 on the front side of each suction hole. A suction reed valve (not shown) that allows only flow is provided. The valve plate 11 is formed with a plurality of discharge holes (not shown) communicating with the plurality of cylinder bores 17 and the discharge chamber 23, and the rear side of each discharge hole is connected to the discharge chamber 23 from the cylinder bore 17. Discharge reed valves (not shown) that allow flow in only one direction are provided.

  A drive shaft 25 extending in the front-rear direction is rotatably provided in the housing 3 via a plurality of front radial bearings 27 and a rear radial bearing 29. In addition, a pulley 31 is integrally provided at the front end portion of the drive shaft 25, and this pulley 31 is coupled to an engine (an example of an external drive source) via a clutch or the like (not shown). is there. A rear thrust bearing 33 that supports the thrust load of the drive shaft 25 from the rear direction is provided between an appropriate portion of the rear portion of the drive shaft 25 and an appropriate portion of the cylinder block 15.

  A single-headed piston 35 is provided in each cylinder bore 17 so as to be able to reciprocate, and each piston 35 has a pair of shoes 37 on its head.

  A lug plate 39 is integrally provided on the drive shaft 25, and the lug plate 39 is located in the crank chamber 19, and the lug plate 39 has lug plate protruding pieces 41 protruding rearward. I have. It should be noted that between the appropriate location on the inner side surface of the front housing 5 and the appropriate location on the front surface of the lug plate 39, a front that supports the thrust load of the lug plate 39 (in other words, the thrust load of the drive shaft 25) from the front. A thrust bearing 43 is provided.

  A sleeve 45 is provided between the lug plate 39 and the rear thrust bearing 33 in the drive shaft 25 so as to be movable in the front-rear direction. The sleeve 45 is located in the crank chamber 19. A front spring 47 is provided between the lug plate 39 and the sleeve 45 in the drive shaft 25 so as to urge the sleeve 45 in the backward direction, and between the sleeve 45 and the rear thrust bearing 33 in the drive shaft 25. Is provided with a rear spring (not shown) that can urge the sleeve 45 forward.

  The sleeve 45 is provided with a swash plate 49 so as to be tiltable in the front-rear direction. In other words, the swash plate 49 tilts in the front-rear direction via the sleeve 45 on the rear side of the lug plate 39 in the drive shaft 25. It is provided as possible. The swash plate 49 includes a swash plate projecting piece 51 that is located in the crank chamber 19 and projects forward. The swash plate projecting piece 51 is connected to the lug plate projecting piece 41 and the connecting pin 53 and It is connected through a long hole 55. Further, the peripheral portion of the swash plate 49 is engaged with a pair of shoes 37 in the plurality of pistons 35 so as to be slidable.

  From the inside of the drive shaft 25 to the valve plate 11 (inside of the drive shaft 25, inside the cylinder block 15, and the valve plate 11), a bleed passage 57 that continuously communicates the crank chamber 19 and the suction chamber 21 is formed continuously. The bleed passage 57 has a plurality of introduction ports 59 extending in the radial direction of the drive shaft 25 on the inlet side. An air supply passage 61 that communicates between the crank chamber 19 and the discharge chamber 23 extends from the inside of the cylinder block 15 to the inside of the rear housing 9 (inside the cylinder block 15, the valve plate 11, and the rear housing 9). A control valve 63 that is formed continuously and is capable of controlling the valve opening is provided in the air supply passage 61.

  Then, the principal part of the swash plate type compressor 1 of embodiment of this invention is demonstrated.

  As shown in FIGS. 3 (a), 4 (a) and 4 (b), a stopper 65 for restricting the oblique angle of the swash plate 49 is formed on the front surface of the swash plate 49. The rear surface of the plate 39 can be contacted. The inner surface of the stopper 65 has an elliptical arc shape (one of the curved shapes) so that the distance gradually changes from the axis of the drive shaft 25. The inner surface of the stopper 65 is on both sides of the entire region. It has a front passage forming area FA1 farthest from the axis 25c of the drive shaft 25 at all times (including when the piston 35 is in the death stroke state and when in the full stroke state). In the pair of front passage formation areas FA1 on the inner side surface of the stopper 65, a front guide passage 67 that guides oil mist from the inner side surface of the stopper 65 toward the periphery of the swash plate 49 is formed. Furthermore, the entrance of each front guide passage 67 is more than the tip of the stopper 65 when the stopper 65 is brought into contact with the rear surface of the lug plate 39 (in other words, when the swash plate 49 is in a full stroke state). Each is separated from the axis of the drive shaft 25.

  Note that, by changing the position of the front passage forming area FA1 on the inner surface of the stopper 65, the outlet of the front guide passage 67 approaches the front high load area LA1 in the peripheral portion of the swash plate 49 as shown in FIG. It doesn't matter if you do. Here, the front high load area LA1 is the frontmost of the entire front area around the swash plate 49 when the stopper 65 is brought into contact with the rear surface of the lug plate 39. It is an area that receives a high load from.

  As shown in FIGS. 3B and 6, an annular protrusion 69 is formed on the rear surface of the swash plate 49, and the distance between the inner surface of the protrusion 69 and the axis 25 c of the drive shaft 25 gradually changes. In this way, it has an elliptical arc shape and symmetrically has a pair of rear passage forming areas FA2 that are always farthest from the axis of the drive shaft 25. A rear guide passage 71 that guides oil mist from the inner side surface of the projection 69 toward the periphery of the swash plate 49 is formed in the pair of rear passage formation regions FA2 on the inner side surface of the projection 69. Furthermore, the outlet of one rear guide passage 71 is close to the rear high load area LA2 in the periphery of the swash plate 49. Here, the rear high load area LA2 is the rearmost of the entire rear surface area of the peripheral portion of the swash plate 49, which is most rearward when the stopper 65 is brought into contact with the rear surface of the lug plate 39. It is an area that receives a high load from.

  Then, the effect | action and effect of embodiment of this invention are demonstrated.

  The lug plate 39 and the swash plate 49 are rotated by rotating the drive shaft 25 by driving the engine, and the plurality of pistons 35 are reciprocated under a stroke corresponding to the oblique angle of the swash plate 49. Thereby, the refrigerant gas sucked from the suction chamber 21 can be compressed in the plurality of cylinder bores 17, and the compressed refrigerant gas can be discharged from the plurality of cylinder bores 17 to the discharge chamber 23. As is well known, during operation of the swash plate compressor 1, the crank chamber 19 is filled with oil mist due to scattering of lubricating oil stored in the crank chamber 19.

  Further, when the cooling load is large during operation of the swash plate compressor 1, the valve opening of the control valve 63 is reduced, and the air is supplied from the discharge chamber 23 to the crank chamber 19 via the air supply passage 61. By reducing the flow rate of the refrigerant gas, the pressure in the crank chamber 19 is reduced, and the differential pressure between the pressure on the front surface side of the piston 35 and the pressure on the rear surface side of the piston is reduced. As a result, while the sleeve 45 is moved forward against the urging force of the front spring 47, the oblique angle of the swash plate 49 can be increased and the stroke of the piston 35 can be increased. On the other hand, when the cooling load is small, the valve opening of the control valve 63 is increased, and the flow rate of the refrigerant gas supplied from the discharge chamber 23 to the crank chamber 19 via the supply passage 61 is increased. Then, the pressure in the crank chamber 19 is increased to increase the differential pressure between the pressure on the front surface side of the piston 35 and the pressure on the rear surface side of the piston 35. As a result, while the sleeve 45 is moved rearward against the urging force of the rear spring, the oblique angle of the swash plate 49 can be reduced and the stroke of the piston 35 can be reduced. Therefore, during the operation of the swash plate compressor 1, the refrigerant gas discharge capacity can be varied according to the cooling load.

  Further, during the operation of the swash plate compressor 1, a part of the oil mist existing in the vicinity of the drive shaft 25 flows along the inner surface of the stopper 65 to the entrance of the front guide passage 67. It is guided from the inner side surface toward the periphery of the swash plate 49 and flows along the inner side surface of the projection 69 to the entrance of the pair of rear guide passages 71. It is guided toward the periphery of the plate 49.

  Here, the inner surface of the stopper 65 has an elliptical arc shape so that the distance gradually changes from the axis 25 c of the drive shaft 25, and out of the entire inner surface area of the stopper 65 from the axis of the drive shaft 25. Since the front guide passage 67 is formed in the front passage formation area FA1 that is always farthest away, the oil mist flowing along the inner surface of the stopper 65 can easily flow into the front guide passage 67 by the action of centrifugal force. . Similarly, the inner surface of the protrusion 69 has an elliptical arc shape so that the distance gradually changes from the axis of the drive shaft 25, and out of the entire inner surface area of the protrusion 69 from the axis 25 c of the drive shaft 25. Since the rear guide passage 71 is formed in the rear passage formation area FA2 that is always farthest away, the oil mist that flows along the inner surface of the protrusion 69 can easily flow into the rear guide passage 71 by the action of centrifugal force. . Thereby, the lubrication efficiency between the shoe 37 and the peripheral part of the swash plate 49 in the plurality of pistons 35 can be increased.

  In particular, when the stopper 65 is brought into contact with the rear surface of the lug plate 39, the entrance of the front guide passage 67 is further away from the axis 25c of the drive shaft 25 than the tip of the stopper 65. It is possible to suppress the oil mist from leaking from the tip portion of the. Further, the front guide passage 67 is formed in the pair of front passage formation areas FA1 on the inner side surface of the stopper 65, and the rear guide passage 71 is formed in the pair of rear passage formation areas FA2 on the inner side surface of the protrusion 69. Oil mist can be supplied over a wide range from the inner surface of 65 toward the front surface of the peripheral portion of the swash plate 49 and from the inner surface of the protrusion 69 toward the rear surface of the peripheral portion of the swash plate 49. Further, since the outlet of one rear guide passage 71 is close to the rear high load area LA2 on the rear surface of the peripheral portion of the swash plate 49, the inner surface of the protrusion 69 and the rear surface of the peripheral portion of the swash plate 49 are provided. Oil mist can be intensively supplied to the rear high load area LA2. Similarly, when the outlet of the front guide passage 67 is close to the front high load area LA1 in the peripheral portion of the swash plate 49 (see FIG. 5), the peripheral portion of the swash plate 49 is formed from the inner surface of the stopper 65. Oil mist can be intensively supplied to the front high load area LA1 on the front surface. Thereby, the lubrication efficiency between the shoe 37 and the peripheral part of the swash plate 49 in the plurality of pistons 35 can be further enhanced.

  As described above, according to the embodiment of the present invention, the lubrication efficiency between the shoe 37 and the peripheral portion of the swash plate 49 in the plurality of pistons 35 can be further increased, so the shoe 37 and the swash plate 49 in the piston 35. Thus, the durability of the swash plate compressor 1 can be further improved.

  In addition, this invention is not restricted to description of the above-mentioned embodiment, It can implement in a various aspect. Further, the scope of rights encompassed by the present invention is not limited to these embodiments.

It is a sectional side view of the swash plate type compressor which concerns on embodiment of this invention, Comprising: The case where a piston exists in a death stroke state is shown. It is a sectional side view of the swash plate type compressor which concerns on embodiment of this invention, Comprising: The case where a piston exists in a full stroke state is shown. FIG. 3A is a perspective view showing a front side portion of the swash plate on which the stopper and the protrusion are formed, and FIG. 3B is a perspective view showing a rear side portion of the swash plate on which the stopper and the protrusion are formed. . 4A is a front view of the swash plate on which the stopper and the protrusion are formed, and FIG. 4B is a side sectional view of the swash plate on which the stopper and the protrusion are formed. It is a front view of the swash plate of another aspect in which the stopper and protrusion were formed. It is a rear view of the swash plate in which the stopper and protrusion were formed.

Explanation of symbols

FA1 Front passage formation area FA2 Rear passage formation area LA1 Front high load area LA2 Rear high load area 1 Swash plate compressor 3 Housing 17 Cylinder bore 19 Crank chamber 21 Suction chamber 23 Discharge chamber 25 Drive shaft 35 Piston 39 Lug plate 49 Swash plate 65 Stopper 67 Front guide passage 69 Projection 71 Rear guide passage

Claims (9)

In the swash plate compressor (1) for compressing gas,
It has a cylinder bore (17) inside, has a crank chamber (19) on the front side of the cylinder bore (17) inside, and communicates with the rear side of the cylinder bore (17) inside the cylinder bore (17). A housing (3) having a suction chamber (21) and a discharge chamber (23);
A drive shaft (25) rotatably provided in the housing (3) and extending in the front-rear direction;
A single-headed piston (35) provided in the cylinder bore (17) so as to be reciprocally movable and having a pair of shoes (37) on the head;
A lug plate (39) provided integrally with the drive shaft (25) and positioned in the crank chamber (19);
The drive shaft (25) is provided on the rear side of the lug plate (39) so as to be tiltable. A swash plate (49) slidably engaged with the pair of shoes (37) in the piston (35);
A stopper (65) provided on the front surface of the swash plate (49), capable of contacting the rear surface of the lug plate (39) and restricting the oblique angle of the swash plate (49),
The inner surface of the stopper (65) has a curved shape so that the distance gradually changes from the axis (25c) of the drive shaft (25). Oil mist from the inner side surface of the stopper (65) toward the peripheral portion of the swash plate (49) in the front passage forming area (FA1) that is always farthest from the axis (25c) of the drive shaft (25) A swash plate compressor characterized in that a front guide passage (67) for guiding the air is formed.   When the stopper (65) is brought into contact with the rear surface of the lug plate (39), the entrance of the front guide passage (67) is located on the drive shaft (25) more than the tip of the stopper (65). 2. The swash plate compressor according to claim 1, wherein the swash plate compressor is configured to move away from the shaft center (25c).   An inner side surface of the stopper (65) has a plurality of the front passage formation regions (FA1), and the front guide passages are provided in the plurality of front passage formation regions (FA1) on the inner side surface of the stopper (65). (67) is formed, The swash plate type compressor of Claim 1 or Claim 2 characterized by the above-mentioned.   The outlet of the front guide passage (67) is located at the forefront when the stopper (65) is brought into contact with the rear surface of the lug plate (39) in the entire front area of the peripheral portion of the swash plate (49). 3. The swash plate compressor according to claim 1, wherein the swash plate compressor is arranged close to a front high load area (LA1) that is inclined toward the front.   The swash plate compressor according to any one of claims 1 to 4, wherein an inner surface of the stopper (65) has an elliptical arc shape. An annular protrusion (69) provided on the rear surface of the swash plate (49);
The inner surface of the protrusion (69) has a curved shape such that the distance gradually changes from the axis (25c) of the drive shaft (25), and the inner surface of the protrusion (69) Oil mist from the inner surface of the projection (69) toward the peripheral portion of the swash plate (49) in the rear passage formation area (FA2) that is always farthest from the axis (25c) of the drive shaft (25) The swash plate compressor according to any one of claims 1 to 5, wherein a rear guide passage (71) for guiding the air is formed.   An inner side surface of the projection (69) has a plurality of the rear passage formation regions (FA2), and the rear guide passage is provided in the plurality of rear passage formation regions (FA2) on the inner side surface of the projection (69). The swash plate compressor according to claim 6, wherein (71) is formed.   The outlet of the rear guide passage (71) is the rearmost when the stopper (65) is brought into contact with the rear surface of the lug plate (39) in the entire rear surface region of the peripheral portion of the swash plate (49). The swash plate compressor according to claim 6, wherein the swash plate compressor is arranged close to a rear high-load region (LA2) that is inclined toward the rear.   The swash plate compressor according to any one of claims 6 to 8, wherein an inner surface of the protrusion (69) has an elliptical arc shape.

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