JP2018150920A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce manufacturing costs in a compressor which can supply a lubrication oil to a lubrication oil supply area.SOLUTION: In a compressor of the invention, an oil separation mechanism 60, an oil storage chamber 39a, and a supply passage 71 are provided in a housing 1. The supply passage 71 connects the oil storage chamber 39a with a lubrication oil supply area having a pressure lower than that of the oil storage chamber 39a and supplies a lubrication oil in the oil storage chamber 39a to the lubrication oil supply area while reducing the pressure of the lubrication oil. The housing 1 has a first valve formation plate 211 serving as a first housing formation body and a front housing 17 serving as a second housing formation body. A first gasket 65 is provided between the first valve formation plate 211 and the front housing 17. A gap passage 67 is formed between the front housing 17 and a protrusion part 65c of the first gasket 65. In this compressor, at least part of the supply passage 71 is formed by the gap passage 67.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor.

  A conventional compressor is disclosed in FIGS. 1 and 3 of Patent Document 1. FIG. This compressor includes a housing and a compression mechanism. A discharge chamber and a plurality of cylinder bores are formed in the housing. The compression mechanism is accommodated in the housing. Specifically, the compression mechanism is housed in each cylinder bore, a swash plate that can rotate with the drive shaft, a link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the drive axis of the drive shaft, and And a piston that reciprocates at a stroke corresponding to the inclination angle by rotation of the swash plate. That is, this compression mechanism is a swash plate type.

  In this compressor, when the drive shaft rotates, the compression mechanism compresses the refrigerant and discharges it to the discharge chamber. During this time, in the compression mechanism, the discharge capacity per one rotation of the drive shaft can be changed by allowing the link mechanism to change the inclination angle of the swash plate.

JP-A-5-172052

  By the way, in such a compressor, an oil separation mechanism, an oil storage chamber, and a supply path may be provided in the housing. In this case, the lubricating oil is separated from the refrigerant discharged into the discharge chamber by the oil separation mechanism, and the lubricating oil is stored in the oil storage chamber. Then, by connecting the oil storage chamber and the lubricating oil supply region having a pressure lower than that of the oil storage chamber by the supply path, the lubricating oil in the oil storage chamber can be supplied to the lubricating oil supply region while reducing the pressure to a certain extent. .

  However, since it is difficult to provide such a supply path in the housing, the manufacturing cost of such a compressor increases.

  The present invention has been made in view of the above-described conventional situation, and an object to be solved is to realize a reduction in manufacturing cost in a compressor capable of supplying lubricating oil to a lubricating oil supply region.

The compressor of the present invention includes a housing and a compression mechanism that is accommodated in the housing and compresses the refrigerant by the rotation of the drive shaft and discharges the refrigerant into the discharge chamber.
In the housing, an oil separation mechanism that separates lubricating oil from the refrigerant discharged into the discharge chamber;
An oil storage chamber for storing the lubricating oil separated by the oil separation mechanism;
A compressor provided with a supply path that connects the oil storage chamber and a lubricating oil supply region having a pressure lower than that of the oil storage chamber, and supplies the lubricating oil in the oil storage chamber to the lubricating oil supply region while reducing the pressure. In
The housing has a first housing forming body and a second housing forming body joined to the first housing forming body,
Between the first housing forming body and the second housing forming body, a gasket for sealing between the inside and the outside of the housing is provided,
The gasket is annularly located on the outer diameter side of the discharge chamber, and is formed with a protrusion that protrudes toward the first housing forming body,
A gap passage is formed by the second housing forming body and the protrusion,
At least a part of the supply path is formed by the gap path.

  In the compressor of this invention, the gasket is provided between the 1st housing formation body and the 2nd housing formation body. And the protrusion which protrudes toward the 1st housing formation body is formed in the gasket. For this reason, the first housing forming body and the second housing forming body are joined while sandwiching the gasket, so that the protrusion contacts the first housing forming body in the gasket, while the protrusion is the second housing forming body. And no contact. For this reason, a clearance passage is formed by the second housing forming body and the protrusion. Here, since the protrusion is located on the outer diameter side of the discharge chamber and has an annular shape, the clearance passage is also formed in an annular shape on the outer diameter side of the discharge chamber. In this compressor, since at least a part of the supply path is formed by the gap path, the supply path is easily provided in the housing as compared with the case where the entire supply path is formed in the first housing or the second housing. be able to.

  Therefore, according to the compressor of the present invention, the manufacturing cost can be reduced in the compressor capable of supplying the lubricating oil to the lubricating oil supply region.

  The reduced pressure by the supply passage is preferably determined by the distance that the lubricating oil flows through the gap passage. In this case, since the reduced pressure by the supply passage can be adjusted by adjusting the distance that the lubricating oil flows through the gap passage, the lubricating oil in the oil storage chamber can be suitably depressurized and supplied to the lubricating oil supply region. It becomes possible. Further, for example, by providing a fixed throttle in the supply path, foreign substances are less likely to be clogged in the supply path, compared to the case where the lubricant is decompressed.

  The housing may be formed with a discharge chamber, a suction chamber, a swash plate chamber, and a plurality of cylinder bores. The compression mechanism is housed in each cylinder bore, a swash plate that is disposed in the swash plate chamber and rotated together with the drive shaft, a link mechanism that allows the inclination angle of the swash plate to be changed with respect to the direction orthogonal to the drive axis of the drive shaft, and And a piston that reciprocates at a stroke corresponding to the inclination angle by rotation of the swash plate. The discharge chamber may be composed of a first discharge chamber provided on one side of the swash plate and a second discharge chamber provided on the other side of the swash plate. The suction chamber may be composed of a first suction chamber provided on one side of the swash plate and a second suction chamber provided on the other side of the swash plate. Each cylinder bore is provided on one side of the swash plate and communicates with the first discharge chamber and the first suction chamber, and each cylinder bore is provided on the other side of the swash plate and includes a second discharge chamber and a second suction chamber. It can consist of a second cylinder bore in communication. Each piston defines a first compression chamber in the first cylinder bore and reciprocates the first cylinder bore between a top dead center position and a bottom dead center position, and a second compression chamber in the second cylinder bore. And a second head that reciprocates the second cylinder bore between a top dead center position and a bottom dead center position. The link mechanism may be arranged so that the top dead center position of the first head moves more greatly than the top dead center position of the second head as the inclination angle decreases. The housing may be formed with a housing chamber that communicates with the first suction chamber and houses a sealing member that seals between the first suction chamber and the outside of the housing while inserting the drive shaft. And it is preferable that a storage chamber is a lubricating oil supply area | region.

  In this compressor, since the first suction chamber and the storage chamber communicate with each other, it is possible to lubricate between the sealing member and the drive shaft with the lubricating oil contained in the refrigerant flowing through the first suction chamber. Become. Here, in this compressor, as the inclination angle of the swash plate decreases, the link mechanism moves the top dead center position of the first head larger than the top dead center position of the second head. The chamber enters a dormant state where the internal refrigerant is not discharged into the first discharge chamber. As a result, the refrigerant is not sucked from the first suction chamber into the first compression chamber, and the refrigerant does not flow through the first suction chamber. Therefore, if the suspension state of the first compression chamber continues, the sealing member and the drive shaft There is concern about lack of lubrication. In this respect, in this compressor, the lubricating oil is supplied from the oil storage chamber to the storage chamber through the supply path. For this reason, even when the pause state of the first compression chamber continues, insufficient lubrication between the sealing member and the drive shaft hardly occurs.

  According to the compressor of the present invention, the manufacturing cost can be reduced in the compressor capable of supplying the lubricating oil to the lubricating oil supply region.

FIG. 1 is a cross-sectional view showing a state where the inclination angle is minimum in the compressor of the embodiment. FIG. 2 is a cross-sectional view showing a state where the inclination angle is maximum in the compressor of the embodiment. FIG. 3 is a schematic diagram illustrating a control mechanism according to the compressor of the embodiment. FIG. 4 is a cross-sectional view illustrating the AA cross section in FIG. 1 according to the compressor of the embodiment. FIG. 5 is an enlarged cross-sectional view of a main part showing a region X in FIG. 1 according to the compressor of the embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating a state in which the first connection passage communicates with the gap passage in the compressor according to the embodiment. FIG. 7 is a schematic diagram illustrating a supply path and the like according to the compressor of the embodiment.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

  As shown in FIGS. 1 and 2, the compressor according to the embodiment includes a housing 1, a drive shaft 3, and a compression mechanism 100.

  Specifically, this compressor is a variable capacity swash plate compressor. In this compressor, the housing 1 is attached to a vehicle engine (not shown). Thereby, the compressor is arrange | positioned in the engine room ER of the vehicle.

  The housing 1 includes a front housing 17, a rear housing 19, a first cylinder block 21, a second cylinder block 23, a first valve forming plate 211, and a second valve forming plate 231. The front housing 17 is an example of the “second housing forming body” in the present invention. The first valve forming plate 211 is an example of the “first housing forming body” in the present invention.

  In this embodiment, when the housing 1 is attached to the engine of the vehicle, the side where the front housing 17 is located is the front side of the compressor, and the side where the rear housing 19 is located is the rear side of the compressor. It defines the front-rear direction. The housing 1 is attached to the engine of the vehicle with the upper side of the page of FIG. 1 and FIG. 2 as the upper side of the engine room ER and the compressor of the vehicle and the lower side of the page as the lower side of the engine room ER and the compressor of the vehicle. It defines the vertical direction of the compressor in a given state. 4 to 7, the vertical direction and the like are defined corresponding to FIGS. In addition, the front-back direction etc. in an Example are examples, and the attitude | position of the compressor of this invention is suitably changed by the attachment state etc. of the housing 1 with respect to the engine of a vehicle.

  The front housing 17 is formed with a boss 17a protruding forward. A storage chamber 170 is provided in the boss 17a. A shaft seal device 25 is accommodated in the accommodation chamber 170. The shaft seal device 25 is an example of the “sealing member” in the present invention. The front housing 17 is formed with a first suction chamber 27a and a first discharge chamber 29a. As shown in FIG. 4, the first suction chamber 27 a is located on the inner peripheral side of the first housing 17. The first suction chamber 27 a communicates with the storage chamber 170. The first discharge chamber 29a is formed in an annular shape and is located on the outer peripheral side of the first suction chamber 27a.

  Further, as shown in FIGS. 1 and 2, a first connection passage 17 b is formed in the front housing 17. The front end of the first connection passage 17 b opens into the accommodation chamber 170. As shown in FIG. 4, the first connection passage 17 b extends from the accommodation chamber 170 side toward the rear in the front housing 17 while passing the outside of the first discharge chamber 29 b in the front housing 17. As shown in FIG. 6, the rear end of the first connection passage 17b opens to the rear end surface of the front housing 17 on the outer diameter side of the first discharge chamber 29b.

  As shown in FIGS. 1 and 2, the front housing 17 is formed with a first front communication path 18a. The first front communication passage 18 a has a front end communicating with the first discharge chamber 29 a and a rear end opening on the rear end surface of the front housing 17.

  The rear housing 19 is provided with a part of a control mechanism 15 described later. The rear housing 19 includes a second suction chamber 27b, a second discharge chamber 29b, and a pressure adjustment chamber 31. The pressure adjustment chamber 31 is located in the center portion of the rear housing 19. The second suction chamber 27 b is formed in an annular shape and is located on the outer peripheral side of the pressure adjustment chamber 31. The second discharge chamber 29b is also formed in an annular shape and is located on the outer peripheral side of the second suction chamber 27b.

  Further, the rear housing 19 is formed with a first rear communication path 20a. The first rear communication path 20 a has a rear end communicating with the second discharge chamber 29 b and a front end opening on the front end surface of the rear housing 19.

  The first cylinder block 21 is provided between the front housing 17 and the second cylinder block 23. The first cylinder block 21 is formed with a plurality of first cylinder bores 21 a extending in the direction of the drive axis O of the drive shaft 3. The first cylinder bores 21a are arranged at equiangular intervals in the circumferential direction.

  The first cylinder block 21 is formed with a first shaft hole 21b through which the drive shaft 3 is inserted. Further, the first cylinder block 21 is formed with a first recess 21c communicating with the first shaft hole 21b from the rear side of the compressor. The first recess 21c is coaxial with the first shaft hole 21b. The first recess 21c has an inner diameter larger than that of the first shaft hole 21b. A first thrust bearing 35a is provided in the first recess 21c. Further, the first cylinder block 21 is formed with a retainer groove 21d for restricting the opening degree of each suction reed valve 213a described later.

  Further, the first cylinder block 21 is formed with a first communication path 37a and a second front side communication path 18b extending in the front-rear direction. Each of the first communication path 37 a and the second front side communication path 18 b has a front end opened on the front end face of the first cylinder block 21 and a rear end opened on the rear end face of the first cylinder block 21. .

  Further, the first cylinder block 21 is formed with a first oil separation chamber 24 a and a second connection passage 26. The first oil separation chamber 24 a extends forward from the rear end surface of the first cylinder block 21. An oil reservoir 39 is accommodated in the first oil separation chamber 24a. An oil storage chamber 39 a is formed in the oil reservoir 39. The oil reservoir 39 is formed with an outlet 39b that opens to the oil storage chamber 39a.

  The second connection passage 26 extends in the front-rear direction of the first cylinder block 21. The rear end of the second connection passage 26 is connected to the outlet 39b. Accordingly, the second connection passage 26 communicates with the oil storage chamber 39a. The front end of the second connection passage 26 is open to the front end surface of the first cylinder block 21.

  The first valve forming plate 211 is disposed between the front housing 17 and the first cylinder block 21. As shown in FIGS. 5 and 6, the first valve forming plate 211 includes a valve plate 212, a suction valve plate 213, a discharge valve plate 214, and a retainer plate 215.

  As shown in FIGS. 1 and 2, the valve plate 212, the discharge valve plate 214, and the retainer plate 215 are formed with the same number of first suction ports 211a as the first cylinder bores 21a. The valve plate 212 and the intake valve plate 213 are formed with the same number of first discharge ports 211b as the first cylinder bores 21a. Further, the valve plate 212, the suction valve plate 213, the discharge valve plate 214, and the retainer plate 215 are formed with a first suction communication port 211c and a first discharge communication port 211d. Further, as shown in FIG. 5, a communication port 211 e is formed in the valve plate 212, the suction valve plate 213, the discharge valve plate 214 and the retainer plate 215.

  As shown in FIGS. 1 and 2, the suction valve plate 213 is provided on the rear surface of the valve plate 212. The suction valve plate 213 is formed with a plurality of suction reed valves 213a that can open and close each first suction port 211a by elastic deformation. The discharge valve plate 214 is provided on the front surface of the valve plate 212. The discharge valve plate 214 is formed with a plurality of discharge reed valves 214a capable of opening and closing each first discharge hole 211b by elastic deformation. The retainer plate 215 is provided on the front surface of the discharge valve plate 214. The retainer plate 215 regulates the maximum opening of each discharge reed valve 214a.

  The second cylinder block 23 is provided between the first cylinder block 21 and the rear housing 19. The second cylinder block 23 is joined to the first cylinder block 21, thereby forming a swash plate chamber 33 with the first cylinder block 21. The swash plate chamber 33 communicates with the first recess 21c. Thereby, the first recess 21 c constitutes a part of the swash plate chamber 33. The swash plate chamber 33 communicates with the first communication path 37a.

  The second cylinder block 23 is formed with a plurality of second cylinder bores 23 a extending in the direction of the drive axis O of the drive shaft 3. Like the first cylinder bores 21a, the second cylinder bores 23a are arranged at equiangular intervals in the circumferential direction, and are coaxially and paired with the first cylinder bores 21a in the front-rear direction. Each first cylinder bore 21a and each second cylinder bore 23a are formed to have the same diameter. In addition, if the 1st cylinder bore 21a and the 2nd cylinder bore 23a have made a pair, these numbers can be designed suitably. Moreover, you may form in the magnitude | size of a different diameter in each 1st cylinder bore 21a and each 2nd cylinder bore 23a. Furthermore, the axial centers of the paired first cylinder bore 21a and second cylinder bore 23a may be shifted.

  The second cylinder block 23 is formed with a second shaft hole 23b through which the drive shaft 3 is inserted. Although not shown, sliding bearings are provided in the first shaft hole 21b and the second shaft hole 23b, respectively.

  The second cylinder block 23 is formed with a second recess 23c communicating with the second shaft hole 23b from the front side of the compressor. The second recess 23c is coaxial with the second shaft hole 23b. The second recess 23c has an inner diameter larger than that of the second shaft hole 23b. The second recess 23 c is also in communication with the swash plate chamber 33 and constitutes a part of the swash plate chamber 33. A second thrust bearing 35b is provided in the second recess 23c. Further, the second cylinder block 23 is formed with a retainer groove 23d for regulating the opening degree of each suction reed valve 233a described later.

  Further, the second cylinder block 23 is formed with a suction port 330 and a second communication path 37b. The suction port 330 communicates with the swash plate chamber 33 and opens to the outside of the second cylinder block 23. The second communication path 37 b extends in the front-rear direction and communicates with the swash plate chamber 33.

  The second cylinder block 23 is formed with a third front side communication path 18c, a second rear side communication path 20b, a combined flow path 23e, and a discharge port 23f. The third front communication path 18c has a front end that opens to the front end surface of the second cylinder block 23, and a rear end that communicates with the combined flow path 23e. The third front communication path 18c communicates with the second front communication path 18b by joining the first cylinder block 21 and the second cylinder block 23 together. The second rear communication passage 20 b has a front end communicating with the joint channel 23 e and a rear end opening on the rear end surface of the second cylinder block 23.

  Further, the second cylinder block 23 is formed with a second oil separation chamber 24b. The second oil separation chamber 24 b extends rearward from the front end surface of the second cylinder block 23. The second oil separation chamber 24b communicates with the combined flow path 23e at the approximate center in the front-rear direction, and communicates with the discharge port 23f at the rear end side. The second oil separation chamber 24b communicates with the first oil separation chamber 24a by joining the first cylinder block 21 and the second cylinder block 23 together. Thus, in this compressor, the oil separation chamber 24 is formed by the first oil separation chamber 24a and the second oil separation chamber 24b.

  An oil separation mechanism 60 is accommodated in the second oil separation chamber 24b. The oil separation mechanism 60 includes a separator body 61 and a discharge check valve 63. The separator body 61 is formed in a substantially cylindrical shape. Inside the separator body 61, a discharge path 61 a is formed extending in the axial direction from the front end face of the separator body 61 to the rear end face. The discharge path 61a communicates with the second oil separation chamber 24b.

  The discharge check valve 63 includes a case 63a, a valve body 63b, and an urging spring 63c. The case 63 a is joined to the rear end of the separator body 61. Thereby, the separator main body 61 and the discharge check valve 63 are integrated. The case 63a is fixed to the rear side of the second oil separation chamber 24b. As a result, the oil separation mechanism 60 is held in the second oil separation chamber 24 b and thus in the oil separation chamber 24.

  The case 63a includes a valve chamber 630, a first passage 631 that communicates the valve chamber 630 and the discharge passage 61a, and a second passage 632 that communicates the valve chamber 630 and the discharge port 23f. The valve body 63 b and the biasing spring 63 c are disposed in the valve chamber 630. The urging spring 63c urges the valve body 63b toward the first passage 631.

  In the discharge check valve 63, a predetermined valve opening pressure is set. Thus, in the discharge check valve 63, when the pressure in the oil separation chamber 24 is equal to or lower than the valve opening pressure, the valve body 63b moves through the first passage 631 by the biasing force of the biasing spring 63c as shown in FIG. Close. Thereby, the discharge check valve 63 makes the oil separation chamber 24 and the discharge port 23f not communicated. On the other hand, when the pressure in the oil separation chamber 24 becomes larger than the valve opening pressure, the valve body 63b opens the first passage 631 against the biasing force of the biasing spring 63c, as shown in FIG. For this reason, the discharge check valve 63 communicates the oil separation chamber 24 and the discharge port 23f. In addition, the value of the valve opening pressure in the discharge check valve 63 can be set as appropriate. Further, the oil separation mechanism 60 may be composed of only the separator body 61.

  The second valve forming plate 231 is disposed between the rear housing 19 and the second cylinder block 23. The second valve forming plate 231 includes a valve plate 232, a suction valve plate 233, a discharge valve plate 234, and a retainer plate 235.

  The valve plate 232, the discharge valve plate 234, and the retainer plate 235 are formed with the same number of second suction ports 231a as the second cylinder bores 23a. The valve plate 232 and the suction valve plate 233 are formed with the same number of second discharge ports 231b as the second cylinder bores 23a. Further, the valve plate 232, the suction valve plate 233, the discharge valve plate 234, and the retainer plate 235 are formed with a second suction communication port 231c and a second discharge communication port 231d.

  The intake valve plate 233 is provided on the front surface of the valve plate 232. The suction valve plate 233 is formed with a plurality of suction reed valves 233a that can open and close each first suction port 231a by elastic deformation. The discharge valve plate 234 is provided on the rear surface of the valve plate 232. The discharge valve plate 234 is formed with a plurality of discharge reed valves 234a that can open and close each first discharge hole 231b by elastic deformation. The retainer plate 235 is provided on the rear surface of the discharge valve plate 234. The retainer plate 235 regulates the maximum opening of each discharge reed valve 234a.

  In this compressor, the first gasket 65 is provided between the front housing 17 and the first valve forming plate 211, more specifically, between the front housing 17 and the retainer plate 215 of the first valve forming plate 211. Is provided. The first gasket 65 is an example of the “gasket” in the present invention. In FIGS. 1, 2, and 5 to 7, the shape of the first gasket 65 is exaggerated for ease of explanation.

  As shown in FIGS. 5 and 6, the first gasket 65 is formed by providing resin on both surfaces of a metal first plate 651, and has a plate shape and a substantially annular shape. . Thereby, as shown in FIGS. 1, 2, and 7, the first gasket 65 has the first discharge chamber 29a and the first suction chamber 27a arranged on the inner peripheral side. As shown in FIGS. 5 and 6, the first gasket 65 faces the rear side of the compressor, that is, the surface 65 a facing the retainer plate 215, and the front side of the compressor, that is, the rear end surface of the front housing 17. And a back surface 65b.

  Further, the first gasket 65 is formed with a protrusion 65c that protrudes from the surface 65a side toward the retainer plate 215 side. The protrusion 65 c is formed at a position on the outer diameter side of the first discharge chamber 29 a in the first gasket 65, and extends in a ring shape so as to surround the first discharge chamber 29 a along the shape of the first gasket 65. ing. Further, as shown in FIGS. 1 and 2, the first gasket 65 is formed with a first front-side discharge communication port 65 d. In FIG. 7, illustration of the first front discharge communication port 65d and the like is omitted for ease of explanation.

  As shown in FIGS. 5 and 6, in the compressor, the front housing 17 and the first valve forming plate 211 are joined with the first gasket 65 interposed. As a result, the protrusion 65 c comes into contact with the retainer plate 215 on the surface 65 a side of the first gasket 65. And the back surface 65b side of the 1st gasket 65 contacts the rear-end surface of the front housing 17 in the outer peripheral side of the 1st discharge chamber 29a. Thus, the first gasket 65 is sandwiched between the front housing 17 and the first valve forming plate 211, and between the first discharge chamber 29 a and the first suction chamber 27 a and the outside of the housing 1, that is, the first The space between the discharge chamber 29a and the first suction chamber 27a and the engine room ER of the vehicle is sealed.

  Here, since the protrusion 65c is formed on the first gasket 65, the rear end surface of the front housing 17 does not come into contact with the back surface 65b side of the first gasket 65 in the portion where the protrusion 65c exists. As a result, a gap passage 67 is formed between the rear end surface of the front housing 17 and the protrusion 65c. As described above, since the protrusion 65c is located on the outer diameter side of the first discharge chamber 29a and has an annular shape, the gap passage 67 also includes the gap passage 67 as shown in FIG. The first discharge chamber 29a is located on the outer diameter side and is formed in an annular shape surrounding the first discharge chamber 29a.

  As shown in FIGS. 5 and 7, the protrusion 65 c is formed with a first through hole 650 that communicates with the gap passage 67. The 1st through-hole 650 is formed in the position which becomes the upper side of a compressor in the protrusion 65c.

  As shown in FIGS. 5 and 6, in this compressor, a second gasket 66 is provided between the suction valve plate 213 and the front end surface of the first cylinder block 21 in the first valve forming plate 211. . The second gasket 66 is also exaggerated in FIGS. 1, 2, 5, and 6 for ease of explanation.

  As shown in FIGS. 5 and 6, the second gasket 66 is formed by providing a resin on both surfaces of a metal second plate 661 and has a plate shape. Thus, the second gasket 66 has a surface 66 a facing the front end surface of the first cylinder block 21 and a back surface 66 b facing the intake valve plate 213. The second gasket 66 is not formed with a protrusion such as the protrusion 65 c of the first gasket 65.

  As shown in FIG. 5, a second through hole 660 is formed in the second gasket 66. The second through hole 660 is formed in the second gasket 66 at a position on the upper side of the compressor. As shown in FIGS. 1 and 2, the second gasket 66 is formed with a first connection port 66 c. The first connection port 66c is formed at a location on the opposite side of the second through hole 660 with the drive axis O interposed therebetween. Further, the second gasket 66 is formed with a second front side discharge communication port 66d.

  As shown in FIGS. 5 and 6, in this compressor, the first valve forming plate 211 and the first cylinder block 21 are joined with the second gasket 66 interposed. Thus, in the second gasket 66, the entire surface 66a side contacts the front end surface of the first cylinder block 21, and the back surface 69b side contacts the intake valve plate 213 over the entire surface. Thus, the second gasket 66 is sandwiched between the first valve forming plate 211 and the first cylinder block 21, and each first cylinder bore 21a, the first communication path 37a, the swash plate chamber 33, and the engine room ER of the vehicle. Seal between. Note that a protrusion similar to the protrusion 65 c of the first gasket 65 may be formed on the second gasket 66. Further, the second gasket 66 may be formed by providing resin on the suction valve plate 213.

  Thus, in this compressor, the front housing 17 and the first cylinder block 21 are joined via the first valve forming plate 211 and the first and second gaskets 65 and 66. Accordingly, as shown in FIGS. 1 and 2, each first cylinder bore 21a communicates with the first suction chamber 27a through each first suction port 211a. Each first cylinder bore 21a communicates with the first discharge chamber 29a through each first discharge port 211b. The first suction chamber 27a and the first communication path 37a communicate with each other through the first suction communication port 211c and the first connection port 66c. Further, the first front communication path 18a and the second front communication path 18b communicate with each other through the first and second front discharge communication ports 65d and 66d and the first discharge communication port 211d.

  As shown in FIG. 5, the gap passage 67 communicates with the front end of the second connection passage 26 through the first and second through holes 650 and 660 and the communication port 211e. Further, by joining the front housing 17 and the first valve forming plate 211, the rear end of the first connection passage 17 b faces the gap passage 67 as shown in FIG. 6. Thereby, the rear end of the first connection passage 17 b communicates with the gap passage 67 at a position different from the front end of the second connection passage 26. Specifically, the rear end of the first connection passage 17b communicates with the gap passage 67 in the gap passage 67 at a position that is on the lower side of the compressor with respect to the portion where the first through hole 650 is formed. That is, the first connection passage 17 b and the second connection passage 26 are connected through the gap passage 67.

  Thus, in this compressor, the supply passage 71 shown in FIGS. 1 and 2 is formed by the first connection passage 17b, the gap passage 67, the first and second through holes 650 and 660, the communication port 211e, and the second connection passage 26. Has been. The supply path 71 connects the oil storage chamber 39a and the storage chamber 170. That is, in this compressor, the storage chamber 170 is the “lubricating oil supply region” in the present invention.

  In this compressor, the third gasket is provided between the rear housing 19 and the second cylinder block 23, more specifically, between the rear housing 19 and the retainer plate 235 in the second valve forming plate 231. 69 is provided. Further, a fourth gasket 70 is provided between the suction valve plate 233 and the front end surface of the second cylinder block 23 in the second valve forming plate 231. The third and fourth gaskets 69 and 70 are also shown exaggerated in FIGS. 1 and 2 for ease of explanation.

  Although not shown in detail, the third gasket 69 has substantially the same configuration as the first gasket 65, and is formed by providing resin on both surfaces of a metal plate. Thus, the third gasket 69 has the second discharge chamber 29b, the second suction chamber 27b, and the pressure adjustment chamber 31 disposed on the inner peripheral side. The third gasket 69 has a front side of the compressor, that is, a surface 69 a facing the retainer plate 235, and a rear side of the compressor, that is, a back surface 69 b facing the front end surface of the rear housing 19. The third gasket 69 is formed with a first rear side discharge communication port 69d.

  Although not shown in detail, the fourth gasket 70 has substantially the same configuration as the second gasket 66 and is formed by providing resin on both surfaces of a metal plate. The fourth gasket 70 has a plate shape, and has a front surface 70 a facing the rear end surface of the second cylinder block 23 and a back surface 70 b facing the intake valve plate 233. The fourth gasket 70 is formed with a second connection port 70c and a second rear discharge communication port 70d.

  In this compressor, the rear housing 19 and the second valve forming plate 231 are joined with the third gasket 69 interposed. Further, the second valve forming plate 231 and the second cylinder block 23 are joined while the fourth gasket 70 is interposed. Here, like the second gasket 66, the third and fourth gaskets 69 and 70 are not formed with a protrusion such as the protrusion 65 c of the first gasket 65. Therefore, in the third gasket 69, the front surface 69 a side is in contact with the retainer plate 235 on the entire surface, and the back surface 69 b side is in contact with the front end surface of the rear housing 19 on the entire surface. Thus, the third gasket 69 is sandwiched between the rear housing 19 and the second cylinder block 23, and the second discharge chamber 29b, the second suction chamber 27b, the pressure adjustment chamber 31, and the engine room ER of the vehicle are connected to each other. Seal the gap. In the fourth gasket 70, the entire surface 70a is in contact with the rear end surface of the second cylinder block 23, and the back surface 70b is in contact with the intake valve plate 233 over the entire surface. Thus, the fourth gasket 70 is sandwiched between the second valve forming plate 231 and the second cylinder block 23, and each second cylinder bore 23a, the second communication path 37b, the swash plate chamber 33, and the engine room ER of the vehicle. Seal between. Note that a protrusion similar to the protrusion 65 c of the first gasket 65 may be formed on the third and fourth gaskets 69 and 70. Further, the third gasket 69 may be formed by providing resin on the retainer plate 235. Similarly, the fourth gasket 70 may be formed by providing resin on the suction valve plate 233.

  Thus, in this compressor, the rear housing 19 and the second cylinder block 23 are joined via the second valve forming plate 231 and the third and fourth gaskets 69 and 70. Accordingly, each second cylinder bore 23a communicates with the second suction chamber 27b through each second suction port 231a. Each second cylinder bore 23a communicates with the second discharge chamber 29b through each second discharge port 231b. The second suction chamber 27b and the second communication path 37b communicate with each other through the second suction communication port 231c and the second connection port 70c. In addition, the first rear communication path 20a and the second rear communication path 20b communicate with each other through the first and second rear discharge communication ports 69d and 70d and the second discharge communication port 231d.

  In this compressor, the first and second suction chambers 27a and 27b and the swash plate chamber 33 are provided by the first and second communication paths 37a and 37b, the first and second suction communication ports 211c and 231c, and the first and second connection ports 66c and 70c. And communicate with each other. As described above, the storage chamber 170 communicates with the first suction chamber 27a. Therefore, the pressures in the first and second suction chambers 27a and 27b, the storage chamber 170, and the swash plate chamber 33 are substantially equal. Then, since the low-pressure refrigerant gas that has passed through the evaporator flows into the swash plate chamber 33 through the suction port 330, the swash plate chamber 33, the first and second suction chambers 27a and 27b, and the storage chamber 170 have an oil storage chamber 39a. The pressure is lower than the inside and the first and second discharge chambers 29a and 29b. In this compressor, the swash plate chamber 33, the first and second suction chambers 27a and 27b, the storage chamber 170, and the first and second communication paths 37a and 37b constitute a suction pressure region.

  Further, in this compressor, the first front communication passage 18a, the first and second front discharge communication ports 65d and 66d, the first discharge communication port 211d, the second front communication passage 18b, and the third front communication passage 18c. Thus, the first discharge communication passage 18 is formed. Furthermore, the second discharge communication path 20 is formed by the first rear communication path 20a, the first and second rear discharge communication ports 69d and 70d, the second discharge communication port 231d, and the second rear communication path 20b. . The first discharge communication path 18 and the second discharge communication path 20 communicate with each other through the joint flow path 23e. Thus, the first discharge chamber 29a and the second discharge chamber 29b communicate with each other through the first and second discharge communication paths 18 and the combined flow path 23e. Thus, in this compressor, a discharge pressure region is configured by the first and second discharge chambers 29a and 29b, the first and second discharge communication paths 18 and 20, and the combined flow path 23e. Further, the first discharge chamber 29a communicates with the oil separation chamber 24 through the first discharge communication path 18 and the combined flow path 23e. Similarly, the second discharge chamber 29b communicates with the oil separation chamber 24 through the second discharge communication path 20 and the combined flow path 23e.

  The drive shaft 3 is inserted into the shaft sealing device 25 and the first and second shaft holes 21 b and 23 b in the housing 1. As a result, the drive shaft 3 is supported by the housing 1 and can rotate around the drive axis O parallel to the front-rear direction of the compressor. Further, when the drive shaft 3 is supported by the housing 1, the shaft seal device 25 is inserted into the outside of the front housing 17 with the drive shaft 3 inserted, that is, between the engine room ER of the vehicle and the first suction chamber 27 a. Seal the gap.

  The drive shaft 3 includes a drive shaft main body 30, a first support member 43a, and a second support member 43b. A screw portion 3 a is formed at the front end of the drive shaft 3. The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) via the screw portion 3a.

  The drive shaft main body 30 extends from the front side of the housing 1 toward the rear side in the axial direction. A first small diameter portion 30 a is formed on the front side of the drive shaft main body 30. A second small diameter portion 30 b is formed on the rear side of the drive shaft main body 30. An axial path 3b and a radial path 3c are formed in the drive shaft main body 30. Details of the axial path 3b and the path 3c will be described later.

  The first support member 43 a is formed in a cylindrical shape having the drive axis O of the drive shaft 3 as the central axis. The first support member 43 a is press-fitted into the first small diameter portion 30 a of the drive shaft main body 30. A first flange 430 is formed at the rear end of the first support member 43a.

  The second support member 43b is also formed in a cylindrical shape with the drive axis O of the drive shaft 3 as the central axis. The second support member 43 b is press-fitted to the rear end side of the second small diameter portion 30 b of the drive shaft main body 30. The second support member 43b is formed with a second flange 431 and an attachment portion (not shown) through which a second pin 47b described later is inserted.

  The compression mechanism 100 includes a swash plate 5, a link mechanism 7, a plurality of pistons 9, a plurality of pairs of shoes 11a and 11b, an actuator 13, and a control mechanism 15 shown in FIG. ing. That is, the compression mechanism 100 is a swash plate type.

  As shown in FIGS. 1 and 2, the swash plate 5 has an annular flat plate shape and has a front surface 5a and a rear surface 5b. The front surface 5a corresponds to “one surface” in the present invention, and the rear surface 5b corresponds to “other surface” in the present invention. The front surface 5 a faces the front side of the compressor in the swash plate chamber 33, that is, the front housing 17 side. The rear surface 5 b faces the rear side of the compressor in the swash plate chamber 33, that is, the rear housing 19 side.

  The swash plate 5 has a ring plate 45. The ring plate 45 is formed in an annular flat plate shape, and an insertion hole 45a is formed at the center. The swash plate 5 is attached to the drive shaft main body 30 and disposed in the swash plate chamber 33 by inserting the drive shaft main body 30 through the insertion hole 45a. Further, the ring plate 45 is formed with a groove portion 45b penetrating from the front surface 5a side to the rear surface 5b side of the swash plate 5. A return spring (not shown) is provided around the drive shaft 3 between the ring plate 45 and the second flange 431 of the second support member 43b.

  The link mechanism 7 is provided in the swash plate chamber 33. The link mechanism 7 has a lug arm 49. The lug arm 49 is disposed behind the swash plate 5 in the swash plate chamber 33, and is located between the swash plate 5 and the second support member 43b. The lug arm 49 is formed so as to be substantially L-shaped from the front to the rear. The lug arm 49 has a weight portion 49a. The shape of the weight portion 49a can be designed as appropriate.

  The front end side of the lug arm 49 is connected to the ring plate 45 by the first pin 47a. Thereby, the lug arm 49 is supported by the ring plate 45, that is, the swash plate 5 so as to be swingable around the first swing axis M1 with the first pin 47a as the first swing axis M1. ing.

  The rear end side of the lug arm 49 is connected to the second support member 43b by the second pin 47b. As a result, the lug arm 49 can swing around the second swing axis M2 with respect to the second support member 43b, that is, the drive shaft 3, with the second pivot 47b serving as the second pivot axis M2. It is supported. In addition to the lug arm 49 and the first and second pins 47a and 47b, the link arm 7 and the third pin 47c, which will be described later, constitute the link mechanism 7 in the present invention.

  The weight portion 49a is provided to extend to the front end side of the lug arm 49, that is, on the opposite side of the second swing axis M2 with respect to the first swing axis M1. For this reason, the lug arm 49 is supported by the ring plate 45 by the first pin 47 a, so that the weight portion 49 a passes through the groove portion 45 b of the ring plate 45 and faces the front surface of the ring plate 45, that is, the front surface 5 a side of the swash plate 5. To position. Then, the centrifugal force generated when the swash plate 5 rotates around the drive axis O also acts on the weight portion 49a on the front surface 5a side of the swash plate 5.

  In this compressor, the swash plate 5 and the drive shaft 3 are connected by the link mechanism 7 so that the swash plate 5 can rotate together with the drive shaft 3. Further, the both ends of the lug arm 49 swing around the first swing axis M1 and the second swing axis M2, respectively, so that the swash plate 5 moves from the minimum value shown in FIG. 1 to the maximum value shown in FIG. The inclination angle can be changed.

  Each piston 9 has a first head 9a at the front end and a second head 9b at the rear end. That is, each piston 9 is a double-headed piston. Each first head portion 9a is accommodated in each first cylinder bore 21a so as to reciprocate. The first compression chambers 53a are formed in the first cylinder bores 21a by the first heads 9a and the first valve forming plate 211. Each of the second heads 9b is housed so as to reciprocate within the second cylinder bore 23a. The second compression chambers 53b are formed in the second cylinder bores 23a by the second heads 9b and the second valve forming plate 231.

  In addition, an engaging portion 9 c is formed at the center of each piston 9. In each engaging portion 9c, hemispherical shoes 11a and 11b are provided. Each of these shoes 11a and 11b converts the rotation of the swash plate 5 into the reciprocating motion of the piston 9 as a conversion mechanism. Thus, the first heads 9a can reciprocate in the first cylinder bores 21a with a stroke corresponding to the inclination angle of the swash plate 5, and the second heads 9b are secondly moved. It is possible to reciprocate within the cylinder bore 23a.

  Here, in this compressor, the stroke of each piston 9 changes with the change of the inclination angle of the swash plate 5, so that the link mechanism 7 is connected to each of the first head 9 a and each second head 9 b. Move the top dead center position. Specifically, as shown in FIG. 1, the link mechanism 7 is configured so that each first head 9 a is located at a position higher than the top dead center position of each second head 9 b as the inclination angle of the swash plate 5 becomes smaller. Move the top dead center position greatly.

  The actuator 13 is disposed in front of the swash plate 5 in the swash plate chamber 33. More specifically, the actuator 13 is located on the first cylinder block 21 side in the swash plate chamber 33 with respect to the swash plate 5. Thereby, the actuator 13 can enter the first recess 21c.

  The actuator 13 has a moving body 13a, a partitioning body 13b, and a control pressure chamber 13c. The control pressure chamber 13c is formed between the movable body 13a and the partition body 13b.

  The moving body 13a is formed in a substantially cylindrical shape. An insertion hole 130 is provided through the front end of the moving body 13a. A pair of connecting arms 132 is formed at the rear end of the moving body 13a. Each connecting arm 132 extends toward the rear of the compressor. In FIGS. 1 and 2, only one of the connecting arms 132 is shown.

  The drive shaft body 30 is inserted through the insertion hole 130 of the moving body 13a. Thereby, the moving body 13a can rotate together with the drive shaft main body 30, and can move the drive shaft main body 30 in the direction of the drive axis O.

  The partition body 13b is formed in a substantially disc shape having substantially the same diameter as the inner diameter of the moving body 13a. The partition 13b is press-fitted into the drive shaft main body 30. As a result, the partition 13b is fixed to the drive shaft main body 30 and can be rotated together with the drive shaft main body 30. The partition 13b may also be configured to be inserted through the drive shaft main body 30 so as to be movable in the drive axis O direction.

  Thus, the partition 13b is arranged in the moving body 13a, and the periphery thereof is surrounded by the moving body 13a. Thereby, when the moving body 13a moves in the drive axis O direction, the inner peripheral surface of the moving body 13a and the outer peripheral surface of the partitioning body 13b slide.

  And the control body 13c is formed between the mobile body 13a and the division body 13b because the division body 13b is surrounded by the mobile body 13a. The control pressure chamber 13c is partitioned from the swash plate chamber 33 by the movable body 13a and the partition body 13b.

  Each pulling arm 132 and the ring plate 45 are connected by a third pin 47c. As a result, the swash plate 5 is pivotally connected to the moving body 13a around the third axis M3 with the third pin 47c as the third axis M3. Here, the first pin 47a and the third pin 47c are arranged to face each other with the drive shaft body 30 in between. That is, each traction arm 132 is connected to the ring plate 45 on the side opposite to the groove 45b with the drive axis O as a reference. In addition, an inclination-decreasing spring (not shown) is provided around the drive shaft 3 between the partition 13b and the ring plate 45.

  The axial path 3 b extends in the direction of the drive axis O in the drive shaft main body 30. The rear end of the axial path 3 b opens to the rear end surface of the drive shaft main body 30 and communicates with the pressure adjustment chamber 31. The radial path 3 c extends in the radial direction of the drive shaft main body 30 while being connected to the front end of the axial path 3 b, and opens to the outer peripheral surface of the drive shaft main body 30. By providing the actuator 13 in the drive shaft main body 30 as described above, the path 3c opens into the control pressure chamber 13c. Thus, the pressure regulation chamber 31 and the control pressure chamber 13c are communicated with each other by the axial path 3b and the radial path 3c.

  As shown in FIG. 3, the control mechanism 15 has an extraction passage 15a, an air supply passage 15b, a control valve 15c, a fixed throttle 15d, an axial passage 3b, and a radial passage 3c.

  The extraction passage 15a is connected to the pressure adjustment chamber 31 and the second suction chamber 27b. The control pressure chamber 13c, the pressure adjustment chamber 31, and the second suction chamber 27b communicate with each other through the extraction passage 15a, the axial path 3b, and the radial path 3c. The air supply passage 15b is connected to the pressure adjusting chamber 31 and the second discharge chamber 29b. The control pressure chamber 13c, the pressure adjustment chamber 31, and the second discharge chamber 29b are communicated with each other by the air supply passage 15b, the axial path 3b, and the radial path 3c. A fixed throttle 15d is provided in the air supply passage 15b.

  The control valve 15c is provided in the extraction passage 15a. The control valve 15c can adjust the opening degree of the extraction passage 15a based on the pressure in the second suction chamber 27b.

  In this compressor, a pipe connected to the evaporator is connected to the suction port 330 shown in FIGS. 1 and 2, and a pipe connected to the condenser is connected to the discharge port 23f. The condenser is connected to the evaporator via a pipe and an expansion valve. These compressors, evaporators, expansion valves, condensers and the like constitute a refrigeration circuit for a vehicle air conditioner. In addition, illustration of an evaporator, an expansion valve, a condenser, and each piping is abbreviate | omitted.

  In the compressor configured as described above, the swash plate 5 rotates in the compression mechanism 100 when the drive shaft 3 rotates. Thereby, in each piston 9, each 1st head 9a reciprocates within each 1st cylinder bore 21a, and each 2nd head 9b reciprocates within each 2nd cylinder bore 23a. For this reason, the first and second compression chambers 53 a and 53 b change in volume according to the stroke of the piston 9. For this reason, in this compressor, the suction process of sucking the refrigerant gas from the first and second suction chambers 27a and 27b to the first and second compression chambers 53a and 53b, and the refrigerant gas in the first and second compression chambers 53a and 53b. The compression stroke to be compressed and the discharge stroke in which the compressed refrigerant gas is discharged into the first and second discharge chambers 29a and 29b are repeatedly performed.

  During these suction strokes and the like, a piston compression force that reduces the inclination angle of the swash plate 5 acts on the rotating body including the swash plate 5, the ring plate 45, the lug arm 49, and the first pin 47a. If the control mechanism 15 changes the pressure of the control pressure chamber 13c to change the inclination angle of the swash plate 5, the discharge capacity can be controlled by increasing or decreasing the stroke of the piston 9.

  Specifically, in the control mechanism 15 shown in FIG. 3, if the control valve 15c reduces the opening degree of the extraction passage 15a, the pressure of the pressure adjusting chamber 31 increases due to the pressure of the refrigerant gas in the second discharge chamber 29b. The pressure in the control pressure chamber 13c increases. For this reason, the variable differential pressure, which is the differential pressure between the control pressure chamber 13c and the swash plate chamber 33, increases.

  As a result, in this compressor, the moving body 13a moves forward of the drive shaft main body 30 in the direction of the drive axis O from the position shown in FIG. 1 against the compression reaction force acting on the swash plate 5 via each piston 9. It moves toward the side and enters the first recess 21c as shown in FIG. The compression reaction force is a resultant force of piston compression force that acts on the swash plate 5 by each piston 9.

  Thereby, in this compressor, the movable body 13a pulls the swash plate 5 forward of the swash plate chamber 33 in the direction of the drive axis O through each connecting arm 132 and the connecting portion 45c. Therefore, in this compressor, the swash plate 5 swings around the action axis M3. Further, the front end side of the lug arm 49 swings around the first swing axis M1, and the rear end side of the lug arm 49 swings around the second swing axis M2. For this reason, the rear end side of the lug arm 49 moves away from the second flange 431 of the second support member 43b. As a result, the swash plate 5 swings with the operating axis M3 as the operating point and the first swinging axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 5 with respect to the direction orthogonal to the drive axis O of the drive shaft 3 increases, and the stroke of each piston 9 increases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 increases.

  Thus, in a state where the inclination angle of the swash plate 5 is large, the refrigerant gas in the first compression chamber 53a is discharged into the first discharge chamber 29a by opening the discharge reed valve 214a, and in the second compression chamber 53b. The refrigerant gas is discharged into the second discharge chamber 29b by opening the discharge reed valve 234a. That is, the compression work of the refrigerant gas is performed in each of the first compression chamber 53a and the second compression chamber 53b. Then, the refrigerant gas discharged into the first discharge chamber 29a flows into the oil separation chamber 24 through the first discharge communication path 18 and the combined flow path 23e. Similarly, the refrigerant gas discharged into the second discharge chamber 29b flows into the oil separation chamber 24 through the second discharge communication path 20 and the combined flow path 23e.

  Thus, the refrigerant gas that has reached the oil separation chamber 24 swirls around the outer peripheral surface of the separator main body 61 in the oil separation mechanism 60, so that the lubricating oil contained in the refrigerant gas is contained by centrifugal force on the inner peripheral surface of the oil separation chamber 24. To separate. The lubricating oil thus separated from the refrigerant gas is stored in the oil storage chamber 39a. Here, the refrigerant gas is depressurized to a certain extent in the process of turning the outer peripheral surface of the separator body 61 to separate the lubricating oil. Therefore, the oil separation chamber 24 including the oil storage chamber 39a has a higher pressure than the swash plate chamber 33, the first and second suction chambers 27a and 27b, and the storage chamber 170, but the first discharge chamber 29a and the second discharge chamber 29b. Low pressure compared to However, even if the oil separation chamber 24 has a lower pressure than the first discharge chamber 29a and the second discharge chamber 29b as described above, the pressure of the oil separation chamber 24 is discharged in a state where the inclination angle of the swash plate 5 is large. The valve opening pressure set for the check valve 63 is exceeded. For this reason, in the discharge check valve 63, the valve body 63b opens the first passage 631 against the urging force of the urging spring 63c, thereby communicating the oil separation chamber 24 and the discharge port 23f. Thereby, the refrigerant gas in the oil separation chamber 24 from which the lubricating oil has been separated passes from the discharge passage 61a in the separator body 61 through the first passage 631, the valve chamber 630, and the second passage 632 of the discharge check valve 63. It is discharged from the discharge port 23f to the condenser via a pipe.

  Further, in this compressor, the oil storage chamber 39 a and the storage chamber 170 are connected by a supply path 71. As a result, the lubricating oil stored in the oil storage chamber 39a can be supplied into the storage chamber 170 while reducing the pressure to a predetermined pressure. Specifically, as shown in FIG. 7, the lubricating oil in the oil storage chamber 39 a flows out from the outflow port 39 b and flows through the second connection channel 26. The lubricating oil reaches the upper side of the compressor in the clearance passage 67 through the second through hole 660, the communication port 211e, and the first through hole 650. As a result, as indicated by the solid line arrow in the figure, the lubricating oil makes a quarter turn in the gap passage 67 from the upper side to the lower side of the compressor, and passes from the gap passage 67 to the first connection passage. It flows out to 17b. Here, the lubricating oil is depressurized to a predetermined pressure in the process of flowing through the gap passage 67. That is, in this compressor, the reduction pressure of the lubricating oil by the supply passage 71 is determined by the distance when the lubricating oil flows through the gap passage 67. In this way, the lubricating oil that has been depressurized to a predetermined pressure is supplied from the first connection passage 17b into the accommodation chamber 170, and the shaft seal device 25 and the drive shaft 3 are lubricated.

  Further, as the refrigerant gas is compressed in the first compression chamber 53a, as described above, the refrigerant gas is sucked from the first suction chamber 27a into the first compression chamber 53a in the suction step. For this reason, the refrigerant gas from the swash plate chamber 33 toward the first compression chamber 53a flows in the first suction chamber 27a. Here, in this compressor, the first suction chamber 27a and the storage chamber 170 communicate with each other. As a result, in this compressor, while the compression work of the refrigerant gas is performed in the first compression chamber 53a, the shaft seal device 25 is driven by the lubricating oil contained in the refrigerant gas flowing in the first suction chamber 27a. Lubrication between the shaft 3 is possible.

  On the other hand, in this compressor, in the control mechanism 15 shown in FIG. 3, when the control valve 15c increases the opening degree of the extraction passage 15a, the pressure in the pressure adjusting chamber 31 and, in turn, the pressure in the control pressure chamber 13c are changed to the second suction chamber. It becomes substantially equal to the pressure of 27b, and the variable differential pressure becomes small.

  Thereby, in this compressor, the swash plate 5 is urged in a direction in which the inclination angle decreases by the compression reaction force acting on the swash plate 5 via each piston 9. Thereby, in this compressor, the swash plate 5 is urged in a direction in which the inclination angle decreases by the compression reaction force acting on the swash plate 5 via each piston 9. For this reason, the movable body 13a is pulled by the swash plate 5 through each connecting arm 132, and the movable body 13a of the actuator 13 moves toward the rear of the swash plate chamber 33 as shown in FIG. As the moving body 13a moves to the rear of the swash plate chamber 33, in this compressor, the swash plate 5 swings around the action axis M3 in the opposite direction to the case where the inclination angle increases. Further, the front end side of the lug arm 49 swings around the first swing axis M1 in the opposite direction to the case where the inclination angle increases, and the rear end side of the lug arm 49 swings around the second swing axis M2. For this reason, the rear end side of the lug arm 49 approaches the second flange 431 of the second support member 43b. As a result, the swash plate 5 swings in the opposite direction to the case where the inclination angle increases with the operating axis M3 as the operating point and the first swinging axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 5 with respect to the direction orthogonal to the drive axis O of the drive shaft 3 decreases, and the stroke of each piston 9 decreases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 decreases.

  Moreover, in this compressor, the centrifugal force which acted on the weight part 49a is also given to the swash plate 5. For this reason, in this compressor, it is easy to displace the swash plate 5 in the direction to reduce the inclination angle.

  In this compressor, the inclination angle of the swash plate 5 is reduced, and the stroke of each piston 9 is reduced, so that the link mechanism 7 moves the top dead center position of each first head 9a greatly. As a result, the top dead center position of each first head 9 a is moved away from the first valve forming plate 211. On the other hand, the link mechanism 7 hardly moves the top dead center position of each second head 9b regardless of the inclination angle of the swash plate 5. Therefore, in this compressor, the compression work of the refrigerant gas is performed in the second compression chamber 53b by the inclination angle approaching the minimum value including the case where the inclination angle of the swash plate 5 is the minimum value. In the first compression chamber 53a, the refrigerant gas inside does not open the discharge reed valve 214a, so that the refrigerant gas does not open in the first discharge chamber. 29a is no longer discharged and enters a resting state. Note that when the first compression chamber 53a is in a resting state, only the refrigerant gas discharged into the second discharge chamber 29b separates the lubricating oil by the separator body 61.

  Here, even when the inclination angle of the swash plate 5 is reduced and the first compression chamber 53 a is in a resting state, the pressure in the oil separation chamber 24 exceeds the valve opening pressure of the discharge check valve 63. As long as the refrigerant gas in the oil separation chamber 24 is discharged from the discharge port 23f to the condenser via a pipe. However, when the inclination angle of the swash plate 5 becomes the minimum value, the refrigerant gas is hardly discharged from the second compression chamber 53b to the second discharge chamber 29b. As a result, the pressure in the oil separation chamber 24 is reduced. The valve opening pressure of the discharge check valve 63 will be lower. Therefore, in the discharge check valve 63, the valve body 63b closes the first passage 631 by the biasing force of the biasing spring 63c, so that the oil separation chamber 24 and the discharge port 23f are not in communication. For this reason, in this compressor, when the inclination angle of the swash plate 5 is the minimum value, even if the drive shaft 3 rotates, the refrigerant gas in the oil separation chamber 24, and consequently, in the second discharge chamber 29b. The refrigerant gas is not discharged from the discharge port 23f to the condenser. Note that while the discharge check valve 63 does not connect the oil separation chamber 24 and the discharge port 23f, the refrigerant gas is prevented from flowing back from the condenser side to the oil separation chamber 24 side through the discharge port 23f.

  Further, since the first compression chamber 53a is in a pause state, in this compressor, the suction reed valve 213a is also not opened, so that the refrigerant gas in the first suction chamber 27a is sucked into the first compression chamber 53a. Nor. For this reason, the refrigerant gas does not flow in the first suction chamber 27a. In this respect, as described above, in this compressor, the oil storage chamber 39a and the storage chamber 170 are connected by the supply passage 71, and the inside of the storage chamber 170 is reduced while reducing the lubricating oil in the oil storage chamber 39a to a predetermined pressure. It is possible to supply to. For this reason, even if the first compression chamber 53a is in a dormant state and the refrigerant gas does not flow through the first suction chamber 27a, the lubricating oil can be supplied from the oil storage chamber 39a to the storage chamber 170 by the supply passage 71. For this reason, in this compressor, even when the suspension state of the first compression chamber 53a continues, such as when the inclination angle of the swash plate 5 is operating at a minimum value, the shaft seal device 25 and the drive shaft 3 Insufficient lubrication is less likely to occur.

  In this compressor, the front housing 17 and the first valve forming plate 211 are joined with the first gasket 65 interposed therebetween, whereby a clearance passage 67 is formed by the front housing 17 and the projection 65c. In this compressor, a part of the supply passage 71 is formed by the gap passage 67, and in the supply passage 71, the first connection passage 17 b and the second connection passage 26 are connected through the gap passage 67. . For this reason, for example, the supply passage 71 is configured by the first connection passage 17b and the second connection passage 26, and the first connection passage 17b and the second connection passage 26 are directly connected to the outer peripheral side of the first discharge chamber 29a. In this compressor, the supply path 71 can be easily provided in the housing 1 as compared with the case where the above is performed.

  Therefore, according to the compressor of the embodiment, the manufacturing cost can be reduced in the compressor capable of supplying the lubricating oil to the storage chamber 170.

  In particular, in this compressor, when the lubricating oil in the oil storage chamber 39 a is supplied into the storage chamber 170, the reduced pressure of the lubricating oil by the supply passage 71 is determined by the distance at which the lubricating oil flows through the gap passage 67. ing. For this reason, in this compressor, it is possible to adjust the reduced pressure by the supply passage 71 by adjusting the distance that the lubricating oil flows through the gap passage 67. For this reason, the lubricating oil in the oil storage chamber 39a can be suitably depressurized to a predetermined pressure and supplied to the storage chamber 170. In addition, by determining the reduced pressure of the lubricating oil through the supply passage 71 based on the distance at which the lubricating oil flows through the clearance passage 67, for example, a fixed throttle is provided in the first connection passage 17b or the second connection passage 26 to obtain a predetermined pressure. Compared with the case where the lubricating oil is depressurized to the pressure, the supply passage 71 is less likely to be clogged with foreign matter.

  While the present invention has been described with reference to the embodiments, it is needless to say that the present invention is not limited to the above-described embodiments and can be appropriately modified and applied without departing from the spirit thereof.

  For example, in the compressor of the embodiment, the supply passage 71 is formed by the first connection passage 17b, the gap passage 67, the first and second through holes 650 and 660, the communication port 211e, and the second connection passage 26. However, the supply path 71 may be formed only by the gap passage 67.

  In the compressor according to the embodiment, the first valve forming plate 211 is used as the first housing forming body, so that the protruding portion 65c of the first gasket 65 protrudes toward the first valve forming plate 211. ing. However, the present invention is not limited thereto, and the front housing 17 may be configured as the first housing forming body so that the protrusion 65c protrudes toward the front housing 17 in the first gasket 65.

  Furthermore, the 1st gasket 65 is provided between the 1st cylinder block 21 and the 2nd cylinder block 23, and the 1st cylinder block 21, the 2nd cylinder block 23, and the protrusion 65c on the back surface 65b side of the 1st gasket 65, The gap passage formed by the above may be used as the supply path 71 or a part of the supply path 71. Similarly, a first gasket 65 is provided between the second cylinder block 23 and the rear housing 19, and is formed by the second cylinder block 23, the rear housing 19, and the protrusion 65 c on the back surface 65 b side of the first gasket 65. The gap path may be used as the supply path 71 or a part of the supply path 71.

  Furthermore, in the compressor of the embodiment, the storage chamber 170 is used as a lubricating oil supply region, and the supply path 71 connects the oil storage chamber 39a and the storage chamber 170. However, the present invention is not limited to this, and the swash plate chamber 33, the first suction chamber 27a, and the second suction chamber 27b are used as a lubricating oil supply region, and the supply path 71 connects the oil storage chamber 39a and the swash plate chamber 33, or the oil storage chamber 39a. And the first suction chamber 27a and the second suction chamber 27b may be connected. Further, the swash plate chamber 33, the first and second suction chambers 27a and 27b, and the storage chamber 170 may all be used as a lubricating oil supply region.

  Furthermore, in addition to the supply path 71 that connects the oil storage chamber 39a and the storage chamber 170, the housing 1 may be provided with a supply path that connects the oil storage chamber 39a and the swash plate chamber 33 and the like.

  Further, the control mechanism 15 may be configured such that a control valve 15c is provided for the air supply passage 15b and a fixed throttle 15d is provided in the extraction passage 15a. In this case, the opening degree of the supply passage 15b can be adjusted by the control valve 15c. Accordingly, the control pressure chamber 13c can be quickly increased in pressure by the pressure of the refrigerant gas in the second discharge chamber 29b, and the discharge capacity can be increased rapidly.

  Further, in the compressor of the embodiment, the inclination angle of the swash plate 5 is changed by adjusting the pressure of the control pressure chamber 13 c of the actuator 13 by the control mechanism 15. However, the present invention is not limited thereto, and the control mechanism 15 may be configured to change the inclination angle of the swash plate 5 by adjusting the pressure in the swash plate chamber 33.

  Furthermore, in the compressor of the embodiment, the swash plate type compression mechanism 100 is adopted, but not limited to this, a vane type compression mechanism or a scroll type compression mechanism may be adopted.

  The present invention can be used for an air conditioner or the like.

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 5 ... Swash plate 7 ... Link mechanism 9 ... Piston 9a ... 1st head 9b ... 2nd head 17 ... Front housing (2nd housing formation body)
21 ... 1st cylinder block (1st housing formation body)
21a ... 1st cylinder bore 23a ... 2nd cylinder bore 25 ... Shaft seal device (sealing member)
27a ... first suction chamber 27b ... second suction chamber 29a ... first discharge chamber 29b ... second discharge chamber 33 ... swash plate chamber 39a ... oil storage chamber 53a ... first compression chamber 53b ... second compression chamber 60 ... oil separation mechanism 65 ... First gasket (gasket)
65c ... Projection 67 ... Clearance passage 71 ... Supply passage 170 ... Storage chamber (lubricating oil supply region)
O ... Drive shaft center

Claims (3)

A housing, and a compression mechanism that is housed in the housing and compresses the refrigerant by rotation of the drive shaft and discharges the refrigerant into the discharge chamber;
In the housing, an oil separation mechanism that separates lubricating oil from the refrigerant discharged into the discharge chamber;
An oil storage chamber for storing the lubricating oil separated by the oil separation mechanism;
A compressor provided with a supply path that connects the oil storage chamber and a lubricating oil supply region having a pressure lower than that of the oil storage chamber, and supplies the lubricating oil in the oil storage chamber to the lubricating oil supply region while reducing the pressure. In
The housing has a first housing forming body and a second housing forming body joined to the first housing forming body,
Between the first housing forming body and the second housing forming body, a gasket for sealing between the inside and the outside of the housing is provided,
The gasket is annularly located on the outer diameter side of the discharge chamber, and is formed with a protrusion that protrudes toward the first housing forming body,
A gap passage is formed by the second housing forming body and the protrusion,
At least a part of the supply passage is formed by the gap passage.   The compressor according to claim 1, wherein the reduced pressure by the supply passage is determined by a distance through which the lubricating oil flows through the gap passage. The discharge chamber, the suction chamber, the swash plate chamber, and a plurality of cylinder bores are formed in the housing,
The compression mechanism includes a swash plate that is disposed in the swash plate chamber and is rotated together with the drive shaft, and a link mechanism that allows a change in an inclination angle of the swash plate with respect to a direction orthogonal to the drive axis of the drive shaft A piston housed in each cylinder bore and reciprocating at a stroke corresponding to the inclination angle by rotation of the swash plate;
The discharge chamber is composed of a first discharge chamber provided on one side of the swash plate and a second discharge chamber provided on the other side of the swash plate,
The suction chamber includes a first suction chamber provided on the one surface side of the swash plate and a second suction chamber provided on the other surface side of the swash plate,
Each cylinder bore is provided on the one surface side of the swash plate and communicates with the first discharge chamber and the first suction chamber, and is provided on the other surface side of the swash plate and the second surface. A second cylinder bore communicating with the discharge chamber and the second suction chamber;
Each of the pistons defines a first compression chamber in the first cylinder bore and reciprocates the first cylinder bore between a top dead center position and a bottom dead center position; and the second cylinder bore A second head for defining a second compression chamber and reciprocating the second cylinder bore between a top dead center position and a bottom dead center position;
The link mechanism is arranged so that the top dead center position of the first head moves more greatly than the top dead center position of the second head as the inclination angle decreases.
The housing is formed with a housing chamber that communicates with the first suction chamber and that houses a sealing member that seals between the first suction chamber and the outside of the housing while inserting the drive shaft. ,
The compressor according to claim 1 or 2, wherein the storage chamber is the lubricating oil supply region.

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