JP2014163328A - Swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a swash plate compressor capable of securing the high degree of freedom in design to actualize a lighter weight while maintaining a compression capacity and also maintaining strength against the compression capacity.SOLUTION: The compressor includes first and second cylinder blocks 17, 19, and first and second thrust bearings 9, 11. In the first cylinder block 17, a plurality of first cylinder bores 17a are formed. In a second cylinder block 19, a plurality of second cylinder bores 19a are formed. A piston 7 has a first piston head 7a for reciprocating in the first cylinder bores 17a, and a second piston head 7b for reciprocating in the second cylinder bores 19a. The first thrust bearing 9 is provided in a first suction chamber 27a, and located outside the first cylinder block 17. The second thrust bearing 11 is provided in a second suction chamber 27b, and located outside the second cylinder block 19.

Description

  The present invention relates to a swash plate compressor.

  Patent Document 1 discloses a conventional swash plate compressor. This swash plate compressor includes first and second cylinder blocks, a front housing, a rear housing, a drive shaft, a swash plate, and a plurality of pistons.

  A plurality of first cylinder bores are formed concentrically at equiangular intervals in the first cylinder block, and the same number of second cylinder bores are formed concentrically at equiangular intervals in the second cylinder block located on the other end side. Has been. Further, the swash plate chamber is formed between the first cylinder block and the second cylinder block. Each first cylinder bore and each second cylinder bore communicate with each other via a swash plate chamber, and each cylinder bore is formed by these.

  Each piston has a first piston head that reciprocates within the first cylinder bore and a second piston head that reciprocates within the second cylinder bore. A first piston head is inserted in the first cylinder bore. As a result, a first compression chamber is defined in the first cylinder bore by the first piston head. A second piston head is inserted into the second cylinder bore. Thus, the second compression bore is defined in the second cylinder bore by the second piston head. Each piston is moored to a swash plate via a pair of shoes, and can reciprocate within the cylinder bore by the swash plate.

  The front housing is coupled to the front end of the first cylinder block. A first valve unit is sandwiched between the front housing and the first cylinder block. A first suction chamber and a first discharge chamber are formed between the front housing and the first valve unit. The first suction chamber and the first discharge chamber communicate with the first compression chamber, respectively.

  The rear housing is coupled to the rear end of the second cylinder block. A second valve unit is sandwiched between the rear housing and the second cylinder block. A second suction chamber and a second discharge chamber are formed between the rear housing and the second valve unit. The second suction chamber and the second discharge chamber communicate with the second compression chamber, respectively.

  The drive shaft passes through the front housing, the first cylinder block, and the second cylinder block, and is provided in the front housing, the first cylinder block, and the second cylinder block. The swash plate is connected to the drive shaft and is housed in the swash plate chamber. The swash plate can be rotated in the swash plate chamber by the rotation of the drive shaft.

  In this swash plate compressor, the first thrust bearing is provided between the first cylinder block and the drive shaft, and the second thrust bearing is provided between the second cylinder block and the drive shaft. . That is, the first thrust bearing and the second thrust bearing are located in a state where the swash plate is sandwiched in the swash plate chamber. The drive shaft is supported in the thrust direction by the first thrust bearing and the second thrust bearing while passing through the front housing, the first cylinder block, and the second cylinder block. In this swash plate compressor, the first thrust bearing and the second thrust support a thrust reaction force acting on each piston during the suction stroke and a thrust force based on a compression reaction force acting on each piston during the compression stroke.

JP 7-197883 A

  By the way, in the swash plate type compressor as described above, in order to improve mountability to a vehicle or the like, a higher degree of design freedom is required in addition to weight reduction while maintaining the compression capacity. On the other hand, in a swash plate type compressor having a constant compression capacity, it is necessary to ensure a certain strength, such as adopting first and second thrust bearings of a predetermined size.

  In this regard, in the conventional swash plate compressor, the first and second thrust bearings are located in the swash plate chamber, that is, inside the piston. For this reason, the first and second thrust bearings must be positioned between the first and second piston heads of each piston, and the axial length is increased. In this case, it is difficult to reduce the weight and size of the swash plate compressor. As a result, an increase in size is inevitable in this swash plate compressor.

  Moreover, in this swash plate type compressor, since the shaft length is large, there is a concern that the strength against torsion or the like is reduced. Here, if it is going to ensure intensity | strength, the thickness of a housing etc. will be thickened, and the further enlargement and weight increase of a swash plate type compressor will be caused. For these reasons, it is difficult to reduce the weight and size of the conventional swash plate compressor.

  Furthermore, since each piston must be present radially outside the first and second thrust bearings, if the axial length of each piston is to be shortened, as long as the volume of each cylinder bore is maintained, The trunk diameter will increase. Also in this case, it becomes difficult to reduce the weight and size of the swash plate compressor. On the other hand, if the volume of each cylinder bore is reduced, the compression capacity of the swash plate compressor cannot be maintained.

  The present invention has been made in view of the above-described conventional circumstances, and can maintain a high compression degree capable of realizing weight reduction while maintaining the compression capacity and maintaining the strength against the compression capacity. Providing a swash plate compressor is a problem to be solved.

The swash plate compressor of the present invention includes a drive shaft, a swash plate coupled to the drive shaft so as to be integrally rotatable, a piston moored to the swash plate, a cylinder block that houses the swash plate therein, A housing coupled to the cylinder block;
The cylinder block is formed with a cylinder bore into which the piston is inserted,
The cylinder bore has a compression chamber defined by the piston,
In the housing, in the swash plate compressor in which a suction chamber and a discharge chamber communicating with the compression chamber are formed,
The drive shaft passes through the cylinder block and is supported in the thrust direction by a first thrust bearing and a second thrust bearing located across the swash plate,
At least one of the first thrust bearing and the second thrust bearing is provided outside the cylinder block and between the housing and the drive shaft (Claim 1).

  In solving the above-mentioned problems, the inventors focused on the position where the first and second thrust bearings are provided, and completed the present invention. That is, in the swash plate compressor of the present invention, at least one of the first thrust bearing and the second thrust bearing is provided between the housing and the drive shaft outside the cylinder block. Thereby, in this swash plate type compressor, at least one of the first thrust bearing and the second thrust bearing is located outside the swash plate chamber. That is, in this swash plate compressor, at least one of the first thrust bearing and the second thrust bearing is positioned outside the piston.

  For this reason, in this swash plate type compressor, it is possible to suppress an increase in the axial length of the piston even when the first and second thrust bearings of a predetermined size are employed to ensure strength. . Further, with this swash plate compressor, it is possible to relax restrictions on the shape of the piston, the drive shaft, and the like.

  Further, in this swash plate compressor, it is possible to reduce the size of the swash plate chamber and hence the entire swash plate compressor by suppressing the increase in the axial length of the piston. For this reason, in this swash plate compressor, it is easy to ensure high strength against torsion and the like.

  Further, in this swash plate compressor, it is not necessary to reduce the volume of the cylinder bore when realizing miniaturization.

  Therefore, according to the swash plate compressor of the present invention, it is possible to ensure a high degree of design freedom that can realize weight reduction while maintaining the compression capacity and the strength against the compression capacity.

  The swash plate compressor of the present invention may be configured with a fixed compression capacity per rotation of the drive shaft, or may be configured to be changeable. If the inclination angle of the swash plate is constant, the compression capacity is fixed, and a fixed capacity type swash plate compressor is obtained. If the inclination angle of the swash plate can be changed, the compression capacity can be changed, and a variable capacity swash plate compressor can be obtained.

  In the swash plate compressor according to the present invention, the housing may be composed of a front housing coupled to the front end of the cylinder block and a rear housing coupled to the rear end of the cylinder block. Further, the cylinder bore may be composed of a first cylinder bore formed on the front side of the cylinder block and a second cylinder bore formed on the rear side of the cylinder block. The piston may have a first piston head that reciprocates within the first cylinder bore and a second piston head that reciprocates within the second cylinder bore. Preferably, the first thrust bearing is provided between the front housing and the drive shaft, and the second thrust bearing is provided between the rear housing and the drive shaft.

  In this case, in the swash plate compressor, both the first thrust bearing and the second thrust bearing are located outside the cylinder block, that is, outside the swash plate chamber. That is, in this swash plate compressor, both the first thrust bearing and the second thrust bearing are located outside the piston. For this reason, in this swash plate type compressor, it becomes possible to realize downsizing more suitably.

  In this swash plate compressor, a compression chamber is formed between the first cylinder bore and the first piston head, and a compression chamber is also formed between the second cylinder bore and the second piston head. For this reason, in this swash plate type compressor, it is possible to ensure a sufficient compression capacity of the refrigerant while realizing miniaturization.

  In the swash plate compressor according to the present invention, at least one of the first thrust bearing and the second thrust bearing has a buffer structure that cooperates with the housing and the drive shaft and can absorb the thrust force by its deformation. (Claim 3).

  In this case, the first thrust bearing and the second thrust bearing are deformed to absorb the thrust force, thereby improving the durability of the first thrust bearing and the second thrust bearing and consequently the durability of the swash plate compressor. It becomes possible to make it. In this case, vibration and abnormal noise can be suppressed.

  It is preferable that at least one of the first thrust bearing and the second thrust bearing faces the suction chamber. In this case, not only the drive shaft but also the first thrust bearing and the second thrust bearing are suitably lubricated by the lubricating oil contained in the refrigerant that may exist in the suction chamber. For this reason, it becomes possible to rotate a drive shaft suitably. In addition, since the wear of the drive shaft and the like is reduced, the durability of the swash plate compressor can be improved. Furthermore, the refrigerant that may be present in the suction chamber is relatively cold. For this reason, in this swash plate compressor, even when frictional heat is generated in the first thrust bearing and the second thrust bearing, cooling with the refrigerant is possible.

  The state in which the first thrust bearing and the second thrust bearing face the suction chamber can be performed, for example, by arranging the first thrust bearing and the second thrust bearing in the suction chamber. Further, the first thrust bearing and the second thrust bearing can be brought into contact with the suction chamber by communicating the first thrust bearing and the second thrust bearing with the suction chamber. In this case, the communication between the suction chamber and the first thrust bearing or the second thrust bearing can be performed by using a gap between the housing and the drive shaft in addition to providing a dedicated communication path.

  According to the swash plate type compressor of the present invention, it is possible to ensure a high degree of design freedom that can realize weight reduction while maintaining the compression capacity and maintaining the strength against the compression capacity.

It is sectional drawing which shows the capacity | capacitance fixed type double-head swash plate type compressor of an Example.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. The fixed capacity double-headed swash plate compressor (hereinafter simply referred to as a compressor) of the embodiment is mounted on a vehicle and constitutes a refrigeration circuit of a vehicle air conditioner.

  As shown in FIG. 1, the compressor includes a first cylinder block 17, a second cylinder block 19, a housing 1, a drive shaft 3, a swash plate 5, a plurality of pistons 7, and a first thrust bearing. 9 and a second thrust bearing 11. The first cylinder block 17 and the second cylinder block 19 correspond to the cylinder block in the present invention.

  The first cylinder block 17 is formed with a plurality of first cylinder bores 17a and a first shaft hole 17b through which the drive shaft 3 is inserted. The first cylinder bores 17a are formed in parallel at equal angular intervals around the first shaft hole 17b. A first sliding bearing 31a is provided in the first shaft hole 17b. The first cylinder block 17 is provided with a suction passage 33a extending in the axial direction. Further, the first cylinder block 17 is formed with a restricting portion (not shown) for restricting the lift amount of each first suction reed valve 21a described later.

  The second cylinder block 19 is located behind the first cylinder block 17. The second cylinder block 19 is formed with the same number of second cylinder bores 19a as the first cylinder bores 17a and a second shaft hole 19b through which the drive shaft 3 is inserted. The second cylinder bores 19a are formed in parallel around the second shaft hole 19b at equal angular intervals. A second sliding bearing 31b is provided in the second shaft hole 19b. The second cylinder block 19 is provided with a suction passage 33b extending in the axial direction. Further, the second cylinder block 19 is formed with a restricting portion (not shown) for restricting the lift amount of each second suction reed valve 23a described later.

  The housing 1 includes a front housing 13 and a rear housing 15.

  The front housing 13 is formed with a boss 13a that protrudes forward. A shaft hole 13b is formed in the boss 13a. A shaft seal device 25 is provided in the shaft hole 13b.

  In the front housing 13, a first suction chamber 27a and a first discharge chamber 29a are respectively formed in an annular shape. The first suction chamber 27 a is located on the inner peripheral side of the front housing 13, and the first discharge chamber 29 a is located on the outer peripheral side of the front housing 13.

  Further, the front housing 13 is formed with a first support portion 13c protruding into the first suction chamber 27a. An annular first pressure receiving seat 13d is recessed in the end surface of the first support portion 13c.

  In the rear housing 15, a second suction chamber 27b and a second discharge chamber 29b are respectively formed in an annular shape. The second suction chamber 27 b is located on the inner peripheral side of the rear housing 15, and the second discharge chamber 29 b is located on the outer peripheral side of the rear housing 15.

  The rear housing 15 is formed with a second support portion 15a that protrudes into the second suction chamber 27b. The end surface of the second support portion 15a is an annular second pressure receiving seat 15b.

  The front housing 13 and the rear housing 15 are fastened by a plurality of through bolts (not shown) in a state where the first cylinder block 17 and the second cylinder block 19 are sandwiched. As a result, the front housing 13 is coupled to the front end of the first cylinder block 17. At this time, the front housing 13 and the first cylinder block 17 are coupled to each other while the first valve unit 21 is sandwiched between the front housing 13 and the front end of the first cylinder block 17. On the other hand, the rear housing 15 is coupled to the rear end of the second cylinder block 19. At this time, the rear housing 15 and the second cylinder block 19 are coupled to each other while the second valve unit 23 is sandwiched between the rear housing 15 and the rear end of the second cylinder block 19.

  As described above, the front housing 13, the first and second cylinder blocks 17 and 19, and the rear housing 15 are coupled, so that the first cylinder block 17 and the second cylinder block 19 are not inclined. A plate chamber 35 is formed. The swash plate chamber 35 and the first suction chamber 27a communicate with each other through a suction passage 33a. The swash plate chamber 35 and the second suction chamber 27b communicate with each other through a suction passage 33b.

  The first valve unit 21 includes a first valve plate 37a, a first intake valve plate 21e, a first discharge valve plate 21f, and a first retainer 39a.

  The same number of first intake ports 21c and first discharge ports 21d as the first cylinder bores 17a are provided through the first valve plate 37a. A plurality of first suction reed valves 21a are formed on the first suction valve plate 21e. Each first suction reed valve 21a opens and closes each first suction port 21c. The first discharge valve plate 21f is formed with a plurality of first discharge reed valves 21b. Each first discharge reed valve 21b opens and closes each first discharge port 21d. The first retainer 39a regulates the lift amount of each first discharge reed valve 21b.

  The second valve unit 23 includes a second valve plate 37b, a second intake valve plate 23e, a second discharge valve plate 23f, and a second retainer 39b.

  The second valve plate 37b is provided with the same number of second suction ports 23c and second discharge ports 23d as the second cylinder bores 19a. A plurality of second suction reed valves 23a are formed on the second suction valve plate 23e. Each second suction reed valve 23a opens and closes each second suction port 23c. A plurality of second discharge reed valves 23b are formed on the second discharge valve plate 23f. Each second discharge reed valve 23b opens and closes each second discharge port 23d. The second retainer 39b regulates the lift amount of each second discharge reed valve 23b.

  The drive shaft 3 includes a first shaft portion 3a located on the front side of the drive shaft 3, a second shaft portion 3b located on the rear side of the drive shaft 3, and a first shaft portion 3a and a second shaft portion 3b. It consists of the 3rd axial part 3c located in between. Further, a screw portion 3d is formed at the tip of the first shaft portion 3a. A pulley and an electromagnetic clutch (both not shown) are connected to the thread portion 3d.

  The first shaft portion 3a and the second shaft portion 3b are formed to have the same diameter. On the other hand, the third shaft portion 3c is formed with a larger diameter than the first shaft portion 3a and the second shaft portion 3b. As a result, an annular third pressure receiving seat 3e is formed between the first shaft portion 3a and the third shaft portion 3c. An annular fourth pressure receiving seat 3f is formed between the third shaft portion 3c and the second shaft portion 3b.

  The drive shaft 3 is inserted from the boss 13a toward the rear of the compressor, passes through the front housing 13 and the first and second cylinder blocks 17 and 19, and the rear end side is located in the rear housing 15. The drive shaft 3 is inserted into the first and second shaft holes 17 b and 19 b in the first and second cylinder blocks 17 and 19. Thus, the distal end side of the first shaft portion 3a is located in the shaft hole 13b, and the rear end side of the first shaft portion 3a and the third pressure receiving seat 3e are located in the first suction chamber 27a. The second shaft portion 3b and the fourth pressure receiving seat 3f are located in the second suction chamber 27b. The third shaft portion 3c is pivotally supported by the first sliding bearing 31a and the second sliding bearing 31b. The drive shaft 3 is rotatable around the rotation axis O in the housing 1 by transmitting power from a pulley or an electromagnetic clutch.

  The swash plate 5 is formed in an annular shape. A boss portion 5 a is formed at the center of the swash plate 5. An insertion hole 5b is provided in the boss portion 5a. The swash plate 5 and the drive shaft 3 are connected by press-fitting the third shaft portion 3c of the drive shaft 3 into the insertion hole 5b. Thereby, the swash plate 5 can be rotated in the swash plate chamber 35 by the rotation of the drive shaft 3.

  Each piston 7 includes a first piston head 7a, a second piston head 7b, and a piston body 7c. The first piston head 7a is formed on the front end side of the piston body 7c. The first piston head 7a is housed in a reciprocating manner in the first cylinder bore 17a, and defines a first compression chamber 41a in the first cylinder bore 17a. The first compression chamber 41a can communicate with the first suction chamber 27a through the first suction port 21c, and can communicate with the first discharge chamber 29a through the first discharge port 21d.

  The second piston head 7b is formed on the rear end side of the piston body 7c. The second piston head 7b is housed in a reciprocating manner in the second cylinder bore 19a, and defines a second compression chamber 41b in the second cylinder bore 19a. The second compression chamber 41b can communicate with the second suction chamber 27b through the second suction port 23c, and can communicate with the second discharge chamber 29b through the second discharge port 23d.

  A recess 7d is formed at the center of the piston body 7c. In the concave portion 7d, hemispherical shoes 43a and 43b that are paired in the front-rear direction are provided. Each piston 7 is anchored to the swash plate 5 through these shoes 43a and 43b.

  In this compressor, each piston 7 reciprocates in the first and second cylinder bores 17a and 19a in accordance with an inclination angle formed by the swash plate 5 with respect to a virtual orthogonal plane orthogonal to the rotation axis O. At that time, the top dead center position of the first piston head 7a in the first compression chamber 41a is set to the point T1 (hereinafter referred to as the top dead center position T1). In this compressor, the top dead center position of the second piston head 7b in the second compression chamber 41b is set at a point T2 (hereinafter referred to as a top dead center position T2).

  The first thrust bearing 9 includes a first race 9a, a second race 9b, a roller 9c sandwiched between the first race 9a and the second race 9b, and a retainer (not shown). A shaft hole 9d is formed on the radial center side of the first race 9a. A shaft hole 9e is formed on the radial center side of the second race 9b.

  The first thrust bearing 9 is provided at a position between the front housing 13 and the drive shaft 3. That is, the first thrust bearing 9 is disposed in the first suction chamber 27a and between the first pressure receiving seat 13d and the third pressure receiving seat 3e. As a result, the first thrust bearing 9 is provided at a position in front of the top dead center position T1 of the first piston head 7a and outside the first cylinder block 17. More specifically, the first race 9a is in contact with the third pressure receiving seat 3e on the center side in the radial direction. Further, the second race 9b is in contact with the first pressure receiving seat 13d on the outer side in the radial direction and is in contact with the shaft seal device 25 on the center side in the radial direction. Thus, the first race 9a abuts against the third pressure receiving seat 3e on the center side in the radial direction, so that when the thrust force is applied, the center side in the radial direction is elastically deformed toward the second race 9b side. Such a configuration of the first race 9a corresponds to the buffer structure in the present invention.

  The second thrust bearing 11 includes a first race 11a, a second race 11b, a roller 11c sandwiched between the first race 11a and the second race 11b, and a retainer (not shown). A shaft hole 11d is formed on the radial center side of the first race 11a. A shaft hole 11e is formed on the radial center side of the second race 11b.

  The second thrust bearing 11 is provided at a position between the rear housing 15 and the drive shaft 3. That is, the second thrust bearing 11 is disposed in the second suction chamber 27b and between the second pressure receiving seat 15b and the fourth pressure receiving seat 3f. Thus, the second thrust bearing 11 is provided at a position behind the top dead center position T2 of the second piston head 7b and outside the second cylinder block 19. More specifically, the first race 11a is in contact with the fourth pressure receiving seat 3f on the radial center side. The second race 11b is in contact with the second pressure receiving seat 15b. Thus, the first race 11a abuts against the fourth pressure receiving seat 3f on the radial center side, so that when the thrust force is applied, the radial center side is elastically deformed toward the second race 11b side. Such a configuration of the first race 11a also corresponds to the buffer structure in the present invention.

  As described above, the first thrust bearing 9 and the second thrust bearing 11 are provided by providing the first thrust bearing 9 in the first suction chamber 27a and the second thrust bearing 11 in the second suction chamber 27b. Is located outside the swash plate chamber 35 on the front and rear sides of the housing 1 with the swash plate 5 interposed therebetween. In addition, according to the magnitude | size of the thrust force which acts on each piston 7, the magnitude | size etc. of the 1st thrust bearing 9 and the 2nd thrust bearing 11 are set suitably.

  The first and second discharge chambers 29a and 29b are a single discharge chamber (not shown), and a condenser is connected to the discharge chamber. The condenser is connected to the evaporator via an expansion valve. The evaporator is connected to the swash plate chamber 35. The swash plate chamber 35 communicates with the first and second suction chambers 27a and 27b through suction passages 33a and 33b. These compressor, condenser, expansion valve and evaporator constitute a refrigeration circuit. In addition, illustration of a condenser, an expansion valve, and an evaporator is abbreviate | omitted.

  In the compressor configured as described above, the drive shaft 3 is rotated by a vehicle engine or motor via a pulley or an electromagnetic clutch. Therefore, each piston 7 reciprocates in the first and second cylinder bores 17a and 19a with a stroke corresponding to the inclination angle of the swash plate 5. Therefore, the refrigerant in the first and second suction chambers 27a and 27b is sucked into the first and second compression chambers 41a and 41b, and the refrigerant compressed in the first and second compression chambers 41a and 41b is first and second compressed. Discharge into the discharge chambers 29a and 29b. The first and second thrust bearings 9 and 11 support the thrust force based on the suction reaction force acting on each piston 7 during the suction stroke and the compression reaction force acting on each piston 7 during the compression stroke.

  Here, in this compressor, the first thrust bearing 9 is arranged in the first suction chamber 27a, so that the first thrust bearing 9 is outside the first cylinder block 17 and on the front side of the compressor. Is located. Further, since the second thrust bearing 11 is disposed in the second suction chamber 27b, the second thrust bearing 11 is located outside the second cylinder block 19 and on the rear side of the compressor. Thus, in this compressor, the first and second thrust bearings 9 and 11 are both located outside the swash plate chamber 35. That is, in this compressor, the first and second thrust bearings 9 and 11 are located outside the pistons 7 respectively.

  For this reason, in this compressor, even if the first and second thrust bearings 9 and 11 having a predetermined size are employed to ensure the strength, for example, each piston 7 due to an increase in the length of each piston body 7c or the like. It is possible to suppress an increase in the shaft length. Thereby, in this compressor, the axial length in the 1st, 2nd cylinder blocks 17 and 19 can be shortened.

  Further, in this compressor, it is possible to relax restrictions on the shapes of the pistons 7, the drive shaft 3, and the like. In particular, in this compressor, it is not necessary to bring the boss portion 5 a of the swash plate 5 into contact with the first and second thrust bearings 9 and 11 in the swash plate chamber 35. For this reason, in this compressor, it is also possible to reduce the size of the boss portion 5a.

  Furthermore, in this compressor, the swash plate chamber 35 is reduced in size by suppressing the increase in the axial length of each piston 7, and thus the compressor as a whole is reduced in size. For this reason, in this compressor, it is easy to ensure high strength against torsion and the like.

  Further, in this compressor, it is not necessary to reduce the volume of the first and second cylinder bores 17a and 19a in order to realize downsizing. Here, in this compressor, it is possible to compress the refrigerant in the first compression chamber 41a and the second compression chamber 41b, respectively. For this reason, in this compressor, it is possible to ensure a certain amount of compression capacity even if the compressor is downsized.

  Therefore, according to the compressor of the embodiment, it is possible to ensure a high degree of design freedom that can realize weight reduction while maintaining the compression capacity and maintaining the strength against the compression capacity.

  In particular, in this compressor, both the first race 9 a of the first thrust bearing 9 and the first race 11 a of the second thrust bearing 11 can be elastically deformed. As a result, the first and second thrust bearings 9 and 11 can absorb the thrust force. For this reason, in this compressor, the durability of the first thrust bearing 9 and the second thrust bearing 11 is high. For this reason, this compressor has high durability and can suppress vibration and abnormal noise during operation.

  Further, in this compressor, a first suction chamber 27a is formed on the inner peripheral side of the front housing 13, and a first discharge chamber 29a is formed outside the first suction chamber 27a, that is, on the outer peripheral side of the front housing 13. Yes. Similarly, a second suction chamber 27 b is formed on the inner peripheral side of the rear housing 15, and a second discharge chamber 29 b is formed on the outer side of the second suction chamber 27 b, that is, on the outer peripheral side of the rear housing 15. The first thrust bearing 9 is provided in the first suction chamber 27a, and the second thrust bearing 11 is provided in the second suction chamber 27b.

  Thus, in this compressor, the first thrust bearing 9 faces the first suction chamber 27a, and the rear end side of the first shaft portion 3a of the drive shaft 3 is in the first suction chamber 27a. It is supported by. Similarly, the second thrust bearing 11 faces the first suction chamber 27b, and the second shaft portion 3b of the drive shaft 3 is supported by the second thrust bearing 11 in the second suction chamber 27b.

  Therefore, in this compressor, not only the drive shaft 3 but also the first and second thrust bearings 9 and 11 are suitably used by the lubricating oil contained in the refrigerant that may exist in the first and second suction chambers 27a and 27b. Lubricated. For this reason, in this compressor, it is possible to rotate the drive shaft 3 suitably. In addition, since the wear of the drive shaft 3 and the like is reduced, this compressor has high durability. Further, in this compressor, even when frictional heat is generated in the first thrust bearing 9 and the second thrust bearing 11, cooling with a refrigerant is possible.

  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 first and second thrust bearings 9 and 11, in addition to the first races 9a and 11a, the second races 9b and 11b may be configured to be elastically deformable.

  Further, only one of the first thrust bearing 9 and the second thrust bearing 11 may be configured to be elastically deformable. Further, both the first thrust bearing 9 and the second thrust bearing 11 may be configured such that elastic deformation is impossible. In these cases, the cost of the compressor can be reduced.

  Further, such a compressor may be configured such that the inclination angle of the swash plate 5 changes so that the compression capacity per one rotation of the drive shaft 3 can be changed. Even in this case, in this compressor, since the first and second thrust bearings 9 and 11 are both located outside the swash plate chamber 35, the inclination angle of the swash plate 5 is changed even if the swash plate chamber 35 is downsized. It is easy to secure the necessary space to do.

  Further, the first thrust bearing 9 may be disposed in the swash plate chamber 35, that is, inside the first cylinder block 17. In this case, in the first cylinder block 17, it is preferable to arrange the first thrust bearing 9 at a position on the front side of the compressor from the top dead center position T1 of the first piston head 7a. Further, instead of the first thrust bearing 9, the second thrust bearing 11 may be disposed in the swash plate chamber 35, that is, inside the second cylinder block 19. Also in this case, it is preferable to arrange the second thrust bearing 11 in the second cylinder block 19 at a position on the rear side of the compressor from the top dead center position T2 of the second piston head 7b.

  Moreover, it is also possible to employ a radial rolling bearing instead of the first sliding bearing 31a or the second sliding bearing 31b.

  Furthermore, you may comprise the compressor of an Example as a single head swash plate type compressor. The compressor in this case may also be configured with a fixed compression capacity or changeable.

  The present invention is applicable to a vehicle air conditioner.

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 5 ... Swash plate 7 ... Piston 7a ... 1st piston head 7b ... 2nd piston head 9 ... 1st thrust bearing 11 ... 2nd thrust bearing 17 ... 1st cylinder block 17a ... 1st cylinder bore 19 Second cylinder block 19a Second cylinder bore 27a First suction chamber 27b Second suction chamber 29a First discharge chamber 29b Second discharge chamber 35 Swash plate chamber 41a First compression chamber (compression chamber)
41b ... Second compression chamber (compression chamber)

Claims (4)

A drive shaft, a swash plate coupled to the drive shaft so as to be integrally rotatable, a piston moored to the swash plate, a cylinder block housing the swash plate therein, and a housing coupled to the cylinder block; With
The cylinder block is formed with a cylinder bore into which the piston is inserted,
The cylinder bore has a compression chamber defined by the piston,
In the housing, in the swash plate compressor in which a suction chamber and a discharge chamber communicating with the compression chamber are formed,
The drive shaft passes through the cylinder block and is supported in the thrust direction by a first thrust bearing and a second thrust bearing located across the swash plate,
A swash plate compressor, wherein at least one of the first thrust bearing and the second thrust bearing is provided outside the cylinder block and between the housing and the drive shaft. The housing comprises a front housing coupled to the front end of the cylinder block and a rear housing coupled to the rear end of the cylinder block,
The cylinder bore comprises a first cylinder bore formed on the front side of the cylinder block and a second cylinder bore formed on the rear side of the cylinder block,
The piston has a first piston head that reciprocates within the first cylinder bore, and a second piston head that reciprocates within the second cylinder bore,
The swash plate type according to claim 1, wherein the first thrust bearing is provided between the front housing and the drive shaft, and the second thrust bearing is provided between the rear housing and the drive shaft. Compressor.   The at least one of the first thrust bearing and the second thrust bearing has a buffer structure that cooperates with the housing and the drive shaft and can absorb the thrust force by its deformation. The described swash plate compressor.   4. The swash plate compressor according to claim 1, wherein at least one of the first thrust bearing and the second thrust bearing faces the suction chamber. 5.

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