JP2009174378A - Variable displacement swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor proving excellent effect without deteriorating mounting properties on a vehicle or the like nor causing other troubles. <P>SOLUTION: In this compressor, a crank chamber 7 and a plurality of cylinder bores 1b are formed out of a cylinder block 1, a front housing 2, and a rear housing 4. A drive shaft 6 is rotatably supported by the cylinder block 1 and the front housing 2 in the crank chamber 7 with one end thereof projected out of the front housing 2. A lug member 10 and the drive shaft 6 synchronize and rotate in the crank chamber 7, and a swash plate 11 is supported by the drive shaft 6 in such a manner that inclination angle thereof can be varied. A thrust plate 8 as a mass is provided on the drive shaft 6 in the crankshaft 7 via an elastic member 9. The thrust plate 8 is loosely fitted on the drive shaft 6 and bears thrust load together with a thrust bearing 5d. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a variable displacement swash plate compressor.

  Conventionally, Patent Document 1 discloses a variable capacity swash plate compressor for vehicle air conditioning. In this compressor, a plurality of cylinder bores are formed in the cylinder block in parallel with the shaft center, and a crank chamber is formed by the cylinder block and the front housing. A rear housing is fixed to the cylinder block via a valve unit, and a suction chamber and a discharge chamber are formed in the rear housing. The front housing, the cylinder block and the rear housing constitute a housing. A piston is accommodated in each cylinder bore so as to be able to reciprocate, and each piston forms a compression chamber in the cylinder bore. Each compression chamber communicates with the suction chamber and the discharge chamber via a valve unit.

  One end of a drive shaft projects from the front housing, and the drive shaft is rotatably supported by the housing in the crank chamber. The crank chamber has the following configuration. First, a lug plate is fixed to the drive shaft, and a thrust bearing is provided between the lug plate and the front housing. A swash plate is supported on the drive shaft so that the tilt angle can be changed. A link mechanism is provided between the lug plate and the swash plate. Specifically, the link mechanism includes a pair of lug arms formed in the lug plate, a guide hole formed in each lug arm, and a pair of guide pins formed in the swash plate. A motion conversion mechanism is provided between the swash plate and each piston. Specifically, the motion conversion mechanism is provided between the shoe sliding surface formed on the front and rear outer peripheral surfaces of the swash plate, the shoe receiving surface formed on each piston, and the shoe sliding surface and the shoe receiving surface. Hemispherical shoe.

  An electromagnetic clutch is provided between the front housing and the drive shaft. The electromagnetic clutch includes a rotor rotatably supported by a front housing via a bearing, a hub coupled to the drive shaft to transmit the rotation of the rotor to the drive shaft, and an armature supported by the hub via an elastic member. The electromagnetic coil is supported by the front housing.

  In this compressor, a belt is wound around a rotor of an electromagnetic clutch, and the rotor is rotationally driven by being driven by an external drive source such as an engine. For this reason, if the electromagnetic coil attracts the armature, the drive shaft rotates together with the rotor via the hub. Therefore, the swash plate performs a swinging motion according to the tilt angle. As a result, the refrigerant gas is sucked into the compression chamber from the suction chamber, and the refrigerant gas is compressed and then discharged into the discharge chamber. During this time, the motion conversion mechanism converts the swinging motion of the swash plate into the reciprocating motion of the piston. Further, the link mechanism makes the swash plate relatively unrotatable with respect to the drive shaft while allowing the tilt angle variation of the swash plate with respect to the drive shaft. Thus, the vehicle air conditioner including the compressor performs air conditioning in the passenger compartment.

  While the drive shaft is rotating, the elastic member of the electromagnetic clutch drives the drive shaft by an external drive source, and uses a rotor, an armature, a hub, etc. as a mass body to dampen vibration caused by rotational fluctuations of the external drive source. It acts to transmit the average torque from the external drive source to the drive shaft. In addition, the elastic member of the electromagnetic clutch also performs a damper action that attenuates vibrations caused by rotational fluctuations based on the suction reaction force and compression reaction force acting on each piston, using a swash plate, a lug plate, a drive shaft, and the like as mass bodies.

  However, the conventional compressor mainly focuses on transmitting the average torque from the external drive source to the drive shaft while the elastic member of the electromagnetic clutch performs the damper action of the external drive source and the damper action of each piston. The spring constant of the elastic member is increased. For this reason, the damper action of each piston is not sufficiently performed, and a certain kind of vibration is transmitted from the compressor to the electromagnetic clutch, and the auxiliary machine such as an alternator is resonated through the rotor and the belt. In this case, silence is desired.

  For this reason, as disclosed in Patent Documents 2 to 4, the elastic member itself is enlarged while increasing the mass of the mass body by increasing the size of the rotor of the electromagnetic clutch or reducing the spring constant of the elastic member of the electromagnetic clutch. It is conceivable to increase the size. Further, as disclosed in Patent Documents 2 and 5, it is conceivable to provide a mass body on the drive shaft through an elastic member in the suction chamber of the compressor. Similarly, it is conceivable to dispose a discharge chamber on the center side of the compressor and to provide a mass body on the drive shaft through an elastic member in the discharge chamber.

JP 2005-83325 A Japanese Patent Laid-Open No. 11-159453 JP 11-159454 A JP 2002-340097 A JP-A-9-317628

  However, the techniques disclosed in Patent Documents 2 to 4 increase the size of the compressor including the electromagnetic clutch, which impairs the ability to be mounted on a vehicle or the like.

  In the techniques disclosed in Patent Documents 2 and 5 and the like, since the mass body is provided inside the partition wall that separates the suction chamber and the discharge chamber, only a mass body having a small diameter can be accommodated, and temporarily in the axial direction. Even if the mass body has a long shape, the effect is small for the increase in weight and physique. Furthermore, in these techniques, the volume of the suction chamber and the discharge chamber is reduced, and the function as a muffler for suction pulsation and discharge pulsation is impaired. If a mass body is provided in the suction chamber, the performance of the compressor may be reduced due to suction resistance. In addition, there are many design restrictions such as providing a mass body while avoiding interference with the valve unit, and assembly and disassembly are difficult, which is not suitable for mass production.

  The present invention has been made in view of the above-described conventional situation, and provides a variable displacement swash plate compressor that exhibits excellent effects without impairing mounting properties on a vehicle or the like and without causing other problems. This is a problem to be solved.

A variable displacement swash plate compressor of the present invention includes a housing that forms a crank chamber and a plurality of cylinder bores, a drive shaft that protrudes from the housing and is rotatably supported by the housing in the crank chamber, A lug member that rotates synchronously with the drive shaft in the crank chamber; a swash plate that is supported by the drive shaft in the crank chamber so as to be capable of varying the tilt angle; and provided between the lug member and the swash plate in the crank chamber. A link mechanism that allows the tilt angle of the swash plate to vary with respect to the drive shaft while preventing the swash plate from rotating relative to the drive shaft, and a piston that is housed in each cylinder bore so as to reciprocate. And a motion conversion mechanism that is provided between the swash plate and each piston in the crank chamber and converts the swinging motion of the swash plate into the reciprocating motion of each piston.
A mass body is provided on the drive shaft in the crank chamber via an elastic member.

  In the compressor of the present invention, while the drive shaft is rotating, the elastic member in the crank chamber cooperates with the mass body in the crank chamber, and vibration due to rotational fluctuation based on the suction reaction force and the compression reaction force acting on each piston. Damper action to attenuate If a pulley capable of exhibiting a damper action is provided between the housing and the drive shaft of the compressor according to the present invention, the pulley performs a damper action for attenuating vibration caused by rotational fluctuations of the external drive source. For this reason, since the pulley transmits the average torque from the external drive source to the drive shaft, the elastic member in the crank chamber can have a spring constant for the damper action of each piston. For this reason, the damper action | operation of each piston is fully performed and it can prevent that a certain kind of vibration resonates an external auxiliary machine from a compressor. For this reason, this compressor can realize high silence.

  The compressor is of a variable displacement swash plate type using a single-headed piston, and a crank chamber is present in a housing that forms the outer shell of the compressor. Since the mass body is provided in the crank chamber via the elastic member, the compressor itself does not increase in size and does not impair the mountability to a vehicle or the like.

  Further, since this compressor is provided with a mass body in a crank chamber having a diameter larger than that of the suction chamber and the discharge chamber located on the axial center side, the mass body can be increased in diameter, and a large damper action can be obtained. It can be demonstrated. Further, according to this compressor, the volume of the suction chamber and the discharge chamber is not reduced, so that the function as a muffler for suction pulsation and discharge pulsation is not impaired. There is no risk of performance degradation due to inhalation resistance. On the contrary, the volume of the crank chamber is reduced, and the response of variable capacity is accelerated.

  Moreover, this compressor has few design restrictions due to the storage of the elastic member and the mass body in the crank chamber. Also, when assembling this compressor, a shaft assembly consisting of a drive shaft, lug member, swash plate, link mechanism, etc. will be prepared, but it is only necessary to provide an elastic member and mass body on this shaft assembly. It is excellent in assembly of the assembly and can be easily disassembled in the case of selective assembly, making it suitable for mass production. Further, since the mass of the thrust bearing is added to the mass body, the damper action is effectively exhibited. Although high-temperature blow-by gas and discharge gas exist in the crank chamber of the variable displacement swash plate compressor, this is not a temperature range in which rubber that can be used as an elastic member cannot exist.

  Therefore, the capacity-variable swash plate compressor of the present invention can exhibit excellent effects without impairing the mountability on a vehicle or the like and without causing other problems.

  In the compressor of the present invention, the lug member may be integrated with the drive shaft or may be a separate member fixed to the drive shaft. When the lug member is integral with the drive shaft, a part of the drive shaft can be used as the lug member.

  In the crank chamber, there may be provided a thrust plate that is fitted in the drive shaft and receives a thrust load, and a thrust bearing provided between the thrust plate and the housing. The mass body is preferably its thrust plate.

  In this case, the thrust plate and the thrust bearing receive a thrust load from the piston. In this case, a shaft assembly including a drive shaft, an elastic member, a thrust plate, a lug member, a swash plate, a link mechanism and the like is prepared, which is suitable for mass production and effectively exhibits a damper action. The conventional lug plate is a lug member and a thrust plate that are fixed to the drive shaft as an integral member.

  By the way, in the link mechanism, there is a request for weight reduction, improvement of torque fluctuation sound due to increase of inertial mass, and inertia for protection of torque limiter due to torque fluctuation when clutchless type compressor is connected to diesel engine. There are demands for contradictory properties such as a reduction in mass. By using a conventional link mechanism that uses a lug plate with an integral thrust plate and lug member, if you try to answer these requirements individually, the number of types of link mechanisms will increase, production facilities will be newly installed, mass production effects will fade, etc. It causes a defect. For this reason, it is preferable that the thrust plate and the lug member are separate members. In this case, the above requirements can be individually answered mainly by changing the material of the thrust plate.

  Further, when the thrust plate and the lug member are separate members, if the thrust plate is loosely fitted to the drive shaft, the inclination of the seat surface of the housing that receives the thrust bearing and the perpendicularity between the thrust plate and the drive shaft It is also possible to eliminate vibrations and noise caused by tolerances.

  The thrust plate may have a weight portion that balances during rotation. In this case, the weight is an effective mass body.

  A bearing is preferably provided between the thrust plate and the lug member. If the thrust plate rotates relative to the drive shaft due to the damping of rotational vibrations, it is not impaired by the bearing.

  The thrust plate is preferably made of a vibration-proof alloy. Anti-vibration alloys absorb vibration by converting vibration energy into heat by internal molecular friction. In addition, the vibration-proof alloy has vibration absorption characteristics that are small in temperature dependence and has a high damping capacity. Moreover, the vibration-proof alloy has a high degree of freedom in shape and excellent durability. For this reason, when changing the material of the thrust plate according to the above requirements, if the thrust plate is an anti-vibration alloy, the vibration transmitted from the piston side is absorbed by the thrust plate and the vibration of the entire compressor is suppressed. Becomes more possible. Anti-vibration alloys include (1) ferromagnetic anti-vibration alloys such as Fe-Cr-Al, Fe-Cr-Al-Mn, Fe-Cr-Mo, Co-Ni, Fe-Cr, and (2) composites. Type Al-Zn anti-vibration alloys, (3) transition type anti-vibration alloys such as Mn-Cu, Cu-Mn-Al, (4) Cu-Zn-Al, Cu-Al-Ni, Ni-Ti, etc. Twin-type vibration-proof alloys can be adopted.

  As a specific configuration of the compressor of the present invention, the thrust plate has an inner peripheral surface, and an elastic member can be fixed to the inner peripheral surface and the outer peripheral surface of the drive shaft. In this case, rubber can be adopted as the elastic member.

  In addition, when the thrust plate has an inner peripheral surface and an elastic member is fixed to the inner peripheral surface and the outer peripheral surface of the drive shaft, the inner surface of the thrust plate extends to the outer peripheral surface side of the drive shaft. One convex portion is provided, and a second convex portion that extends toward the inner peripheral surface side of the thrust plate may be provided on the outer peripheral surface of the drive shaft. The elastic member may be provided between the first convex portion and the second convex portion, and may have an elastic body having an urging force in a direction in which the first convex portion and the second convex portion are moved away from each other. The elastic body may be a spring, rubber, or a spring inserted in rubber.

  In the compressor according to the present invention, the link mechanism is provided between the lug member, one swash plate arm protruding from the swash plate side to the lug member side, and between the lug member and the swash plate arm. It is supported by the lug member around the lug side axis perpendicular to the virtual plane determined by the axis and the top dead center position of the swash plate, and is supported by the swash plate arm around the swash plate axis parallel to the lug side axis. Intermediate arm. In this case, although it has one swash plate arm, it does not have a conventional lug arm. Thus, in this compressor, no noise is generated and the link mechanism operates smoothly.

  The intermediate arm may include a first intermediate arm that extends from the lug member side to the swash plate side, and a second intermediate arm that extends from the lug member side to the swash plate side. The first intermediate arm and the second intermediate arm are pivotally supported by the lug member and the swash plate arm by the lug side pin constituting the lug side axis and the swash plate side pin constituting the swash plate side axis, The lug member and the swash plate arm can be slidably clamped by the plate side pin and fastened.

  In this case, the inner surface of the first intermediate arm is guided by the outer surface of the lug member and one side surface of the swash plate arm, and the inner surface of the second intermediate arm is guided by the outer surface of the lug member and the other side surface of the swash plate arm. . Thus, in this compressor, the processing accuracy of the parallel surfaces of the lug member, the swash plate arm, and the first and second intermediate arms can be lowered, and there is no need to strictly assemble these parts selectively. Therefore, the manufacturing cost can be reduced. Moreover, since it is not necessary to form a lug arm in a lug member, manufacture of a lug member and by extension, manufacture of the whole compressor becomes easy. Furthermore, since the first and second intermediate arms are fastened together by the lug side pin and the swash plate side pin, the first and second intermediate arms do not move individually, and the first and second intermediate arms, The swash plate is difficult to distort and distort from its normal position.

  In the compressor according to the present invention, the motion conversion mechanism includes a shoe sliding surface formed on the front and rear outer peripheral surfaces of the swash plate, a shoe receiving surface formed on each piston, and between the shoe sliding surface and the shoe receiving surface. And a hemispherical shoe. And it is preferable that the swash plate arm is formed avoiding the vertical on the shoe sliding surface. Thus, the swash plate can easily process the shoe sliding surface, and the productivity is improved.

  In the compressor of the present invention, the housing may be equipped with a pulley having a rotor rotatably supported on the housing via a bearing and a hub coupled to the drive shaft and transmitting the rotation of the rotor to the drive shaft. . And it is preferable that a pulley has a damper part between a rotor and a hub. In this case, the damper portion of the pulley performs a damper action that attenuates the vibration caused by the rotational fluctuation of the external drive source. The damper portion of the pulley can be made to have a large spring constant mainly for transmitting the average torque from the external drive source to the drive shaft. Thus, even if the transmission performance of the average torque is increased to reduce the power loss, the effects of the present invention can be exhibited at the same time. The pulley includes a rotor rotatably supported on the front housing via a bearing, a hub coupled to the drive shaft to transmit the rotation of the rotor to the drive shaft, an armature supported by the hub via a damper portion, An electromagnetic clutch including an electromagnetic coil supported by the front housing may be used.

  In the compressor according to the present invention, the housing is mounted with a pulley having a rotor rotatably supported on the housing via a bearing and a hub coupled to the drive shaft and transmitting the rotation of the rotor to the drive shaft. obtain. And it is also preferable that a pulley does not have a damper part between a rotor and a hub. In this case, the pulley directly drives the drive shaft, and the average torque transmission is enhanced. Also in this case, the effects of the present invention can be exhibited at the same time. The pulley is rotatably supported by the front housing via a bearing, a hub coupled to the drive shaft and transmitting the rotation of the rotor to the drive shaft, and supported by the hub so as to be movable in the axial direction. It may be an electromagnetic clutch comprising an armature that does not have an electromagnetic wave and an electromagnetic coil supported by the front housing.

  Embodiments 1 to 3 embodying the present invention will be described below with reference to the drawings.

  As shown in FIG. 1, the variable capacity swash plate compressor according to the first embodiment includes a cylinder block 1, a front housing 2, and a rear housing 4, and the front housing 2 is joined to the front end of the cylinder block 1. The rear housing 4 is joined to the rear end of the cylinder block 1 via the valve unit 3. The cylinder block 1 and the front housing 2 are provided with shaft holes 1a and 2a extending in the axial direction. The shaft holes 1a and 2a are respectively provided with drive shafts 6 via radial bearings 5a and 5b and a shaft seal device 5c. It is supported so that it can rotate. Note that the lower side in FIG. 1 is the front side, and the upper side is the rear side.

  A crank chamber 7 is formed by the front housing 2 and the cylinder block 1. In the crank chamber 7, there are provided a thrust plate 8 fitted to the drive shaft 6 and a thrust bearing 5 d provided between the thrust plate 8 and the front housing 2.

  As shown in FIGS. 2 to 4, the thrust plate 8 is formed concentrically with the drive shaft 6. The thrust plate 8 is formed with a shaft hole 8a having a diameter slightly larger than that of the drive shaft 6, and a cylindrical inner peripheral surface 8b having a diameter larger than that of the shaft hole 8a and positioned in front of the shaft hole 8a. A boss 8c is formed. The front surface of the thrust plate 8 on the outer peripheral side of the boss 8c is a seat surface 8d that receives the thrust bearing 5d. As shown in FIGS. 2 and 4, the rear surface of the thrust plate 8 is a seating surface 8e with which a plain bearing 10c of a lug member 10 described later contacts, and the outer peripheral side of the seating surface 8e is rearward of the seating surface 8e. The weight portion 8f protrudes into the center. The weight portion 8f according to the first embodiment is formed in an annular shape, but may be formed in a non-annular shape in order to eliminate rotational unbalance of the link mechanism 12 described later. The thrust plate 8 is made of a vibration-proof alloy.

  As shown in FIGS. 2 to 4, an elastic member 9 made of rubber is press-fitted between the inner peripheral surface 8 b of the thrust plate 8 and the outer peripheral surface of the drive shaft 6. The elastic member 9 can be fixed between the inner peripheral surface 8b and the outer peripheral surface of the drive shaft 6 by vulcanization.

  As shown in FIGS. 2 and 4, the drive shaft 6 is provided with a lug member 10 behind the thrust plate 8. The lug member 10 is formed with a press-fitting hole 10d, and the drive shaft 6 is press-fitted into the press-fitting hole 10d. The lug member 10 has a plain bearing 10c on the thrust plate 8 side. The lug member 10 is formed in a horseshoe shape having parallel surfaces 10a on the back side on the top dead center side. Further, on the top dead center side of the lug member 10, an insertion hole 10 b orthogonal to both the parallel surfaces 10 a is recessed. Both insertion holes 10b are formed to have a slightly larger diameter than the lug-side pin 23 described later.

  As shown in FIG. 1, a swash plate 11 is provided in the crank chamber 7 behind the lug member 8. Flat shoe sliding surfaces 11 a are formed on the front and rear outer peripheral surfaces on the outer peripheral side of the swash plate 11. The swash plate 11 is inserted through the drive shaft 6, and the inclination angle is changed by the link mechanism 12 provided between the swash plate 11 and the lug member 10 in this state. One support portion 11e protrudes from the bottom dead center side of the surface of the swash plate 11 toward the lug member 10 toward the lug member 10, and the support portion 11e is connected to the rear surface of the lug member 10 when the swash plate 11 is at the maximum inclination angle. It comes to contact.

  The cylinder block 1 is provided with a plurality of cylinder bores 1b extending concentrically extending in the axial direction. A single-headed piston 13 is accommodated in each cylinder bore 1b so as to be able to reciprocate. A shoe receiving surface 13a, which is recessed in a spherical shape, is provided on the neck portion of each piston 13 so as to face each other. A pair of front and rear shoes 14 is provided between the swash plate 11 and each piston 13. Each shoe 14 has a substantially hemispherical shape. The front and rear shoe sliding surfaces 11a, the front and rear shoe receiving surfaces 13a, and the front and rear shoes 14 constitute a motion conversion mechanism.

  An annular suction chamber 4a is formed on the outer peripheral side of the rear housing 4, and a discharge chamber 4b separated from the suction chamber 4a by a partition wall 4e is formed on the inner peripheral side thereof. The cylinder bore 1 b can communicate with the suction chamber 4 a via the suction valve mechanism of the valve unit 3 and can communicate with the discharge chamber 4 b via the discharge valve mechanism of the valve unit 3.

  Further, a capacity control valve 15 is accommodated in the rear housing 4. The capacity control valve 15 communicates with the suction chamber 4a through the detection passage 4c, and the discharge chamber 4b and the crank chamber 7 communicate with each other through the air supply passage 4d, which is shown only partially. The capacity control valve 15 detects the pressure in the suction chamber 4a, thereby changing the opening degree of the air supply passage 4d and changing the discharge capacity of the compressor. Further, the crank chamber 7 and the suction chamber 4a communicate with each other through an extraction passage (not shown). A condenser 17, an expansion valve 18 and an evaporator 19 are connected to the discharge chamber 4 b by a pipe 16, and the evaporator 19 is connected to the suction chamber 4 a by a pipe 16.

  As shown in FIGS. 2 and 4, the link mechanism 12 is integrated with the lug member 10 and the swash plate 11, and has one swash plate arm 11b that protrudes toward the lug plate 8 on the top dead center side. An intermediate arm 20 is provided between the lug member 10 and the swash plate arm 11b. The intermediate arm 20 includes plate-like first and second intermediate arms 21 and 22 extending from the lug member 10 side to the swash plate 11 side, two lug side pins 23, and one swash plate side pin 24. .

  As shown in FIG. 4, the first intermediate arm 21 extends in parallel with a virtual plane P determined by the center axis of the drive shaft 6 and the top dead center position of the swash plate 9, and forms a pair and faces the back. 1 The guided surfaces 21 a and 21 b are provided in the front and rear in the rotational direction R of the drive shaft 6. The second intermediate arm 22 extends parallel to the virtual plane P, and has second guided surfaces 22 a and 22 b that are paired with each other on the back and forth in the rotational direction R of the drive shaft 6.

  Further, press-fitting holes 21c and 21d are provided at both ends of the first intermediate arm 21 at right angles to the first guided surfaces 21a and 21b, and second guided surfaces 22a and 22b are formed at both ends of the second intermediate arm 22, respectively. Press-fitting holes 22c and 22d are provided at right angles. The press-fitting holes 21 c and 22 c have a press-fitting allowance for the lug-side pin 23, and the press-fitting holes 21 d and 22 d have a press-fitting allowance for the swash plate side pin 24.

  The swash plate arm 11b is formed to have substantially the same width as that between both parallel surfaces 10a of the lug member 10, and has parallel surfaces 11c that are back to each other. The swash plate arm 11b is provided with an insertion hole 11d perpendicular to both parallel surfaces 11c. The insertion hole 11 d has a slightly larger diameter than the swash plate side pin 24.

  Both insertion holes 10b of the lug member 10 and both press-fitting holes 21c, 22c of the first and second intermediate arms 21, 22 extend in the direction of the lug side axis A1 orthogonal to the virtual plane P. The insertion hole 11d of the swash plate arm 11b and the press-fitting holes 21d and 22d of the first and second intermediate arms 21 and 22 extend in the direction of the swash plate side axis A2 parallel to the lug side axis A1.

  The first and second intermediate arms 21 and 22 are pivotally supported by the lug member 10 and the swash plate arm 11b by the lug side pin 23 and the swash plate side pin 24, and the lug by the lug side pin 23 and the swash plate side pin 24. The member 10 and the swash plate arm 11b are slidably clamped and fastened. More specifically, both lug-side pins 23 are press-fitted into the first and second intermediate arms 21 and 22 while being loosely fitted to the lug member 10, and the swash plate-side pins 24 are first fitted while being loosely fitted to the swash plate arm 11b. 2 It is press-fitted into the intermediate arms 21 and 22. The lug side pin 23 constitutes the lug side axis A1, and the swash plate side pin 24 constitutes the swash plate side axis A2. The swash plate arm 11b is formed so as to avoid the vertical top of the shoe sliding surface 11a.

  Further, as shown in FIG. 1, a pulley 50 is provided between the front housing 2 and the drive shaft 6. The pulley 50 includes a hub 51, a plurality of damper members 52, a rotor 53, and a weight member 54.

  The front housing 2 of the compressor has a boss 2b that projects the drive shaft 6 inward, and the hub 51 of the pulley 50 is provided with a hub body 51a that is coaxial with the drive shaft 6 in the boss 2b. . The hub body 51a is screwed to the drive shaft 6. The hub 51 integrally has a first disc portion 51c extending in a disc shape from the hub body 51a in a radially outward direction. The hub main body 51a and the first disc part 51c are made of metal.

  A plurality of concentric holes 51d are formed through the first disc portion 51c, and a bridge 51e is formed between the holes 51d. Each bridge 51e is a torque limiter portion that breaks when the torque transmitted from the rotor 53 becomes equal to or higher than the set torque. Further, on the outer peripheral side of the first disc portion 51c, a resin-made second disc portion 51f formed integrally with the hub main body 51a and the disc portion 51c is provided. The second disc portion 51f is provided with a plurality of convex pieces 51g extending vertically from the first disc portion 51c toward the rear. A disc-shaped weight member 54 is integrally provided on the front surface of the hub body 51a.

  The rotor 53 includes a cylindrical rotor main body 53a and a resin rotating portion 53b formed integrally with the rotor main body 53a. A radial bearing 30 is provided between the outer peripheral surface of the boss 2b of the front housing 2 of the compressor and the rotor body 53a. An annular recess 53c is formed concentrically on the front surface of the rotating portion 53b, and a plurality of pieces of partition walls 53d extending vertically from the bottom face toward the front are provided at equal intervals in the recess 53c. A plurality of damper members 52 having left and right dampers straddling the partition wall 53d are housed in the recesses 53c. Each damper member 52 is made of rubber having a large spring constant. The convex pieces 51g of the hub 51 are inserted between the damper members 52. The pulley 50 is known from Japanese Patent Application Laid-Open No. 2004-144226.

  The belt 32 is wound around the rotating portion 53 b of the rotor 53. The belt 32 is also wound around other auxiliary machines such as an engine, an alternator, a water jacket pump, and a power steering pump, which are also drive sources of the vehicle.

  In the compressor configured as described above, the belt 32 rotates the rotor 53 of the pulley 50 by driving the engine. The rotation of the rotor 53 is transmitted to the hub 51 via each damper member 52, and the drive shaft 6 is driven in the rotation direction R. For this reason, the lug member 10 and the swash plate 11 rotate synchronously, and the piston 13 reciprocates in the cylinder bore 1b via the shoe 14. Thereby, the volume of the compression chamber formed on the head side of the piston 13 changes. For this reason, the refrigerant gas in the suction chamber 4a is sucked into the compression chamber and compressed, and then discharged into the discharge chamber 4b. In this way, the refrigeration operation is performed in the refrigeration circuit including the compressor, the condenser 17, the expansion valve 18, and the evaporator 19. During this time, the motion conversion mechanism converts the swing motion of the swash plate 11 into the reciprocating motion of the piston 13. Further, the link mechanism 12 makes the swash plate 11 relatively unrotatable with respect to the drive shaft 6 while allowing the tilt angle variation of the swash plate 11 to the drive shaft 6.

  While the drive shaft 6 is rotating, the thrust plate 8 and the thrust bearing 5 d receive a thrust load from the piston 13. The elastic member 9 in the crank chamber 7 cooperates with the thrust plate 8 to perform a damper action that attenuates vibration due to rotational fluctuations based on the suction reaction force and compression reaction force acting on each piston 13.

  Further, in the pulley 50, each damper member 52 positioned between the rotor 53 and the hub 51 performs a damper action that attenuates vibration due to engine rotational fluctuation. For this reason, since the pulley 50 suitably transmits the average torque from the engine to the drive shaft 6, the elastic member 9 in the crank chamber 7 can have a spring constant for the damper action of each piston 13. For this reason, the damper action | operation of each piston 13 is fully performed, and a certain kind of vibration does not resonate an external auxiliary machine from a compressor. For this reason, this compressor can realize high silence.

  Further, this compressor is of a capacity variable type swash plate type using a single-headed piston 13, and a crank chamber 7 exists in the front housing 2 that forms the outline of the compressor. Since the thrust plate 8 is provided in the crank chamber 7 via the elastic member 9, the compressor itself does not increase in size, and the mountability to the vehicle is not impaired.

  In addition, since the compressor is provided with a mass body in the crank chamber 7 having a diameter larger than that of the discharge chamber 4b located on the axial center side, the diameter of the thrust plate 8 can be increased and a large damper action can be achieved. Can be demonstrated. Furthermore, according to this compressor, the volume of the suction chamber 4a and the discharge chamber 4b is not reduced, so that the function as a muffler for suction pulsation and discharge pulsation is not impaired. There is no risk of performance degradation due to inhalation resistance. On the contrary, the volume of the crank chamber 7 is reduced and the response of variable capacity is accelerated.

  Further, this compressor has few design restrictions due to the storage of the elastic member 9 and the thrust plate 8 in the crank chamber 7. Further, when the compressor is assembled, a shaft assembly including the drive shaft 6, the lug member 10, the swash plate 11, the link mechanism 12 and the like is prepared, and the elastic member 9 and the thrust plate 8 are provided on the shaft assembly. Therefore, the assembly of the shaft assembly is excellent, and it is easy to disassemble in the case of selective assembly, and is suitable for mass production. Further, since the mass of the thrust bearing 5d is also added to the thrust plate 8, the damper action is effectively exhibited.

  Therefore, this compressor can produce excellent effects without impairing the mountability to the vehicle and without causing other problems.

  In this compressor, since the thrust plate 8 and the lug member 10 are separate members and the thrust plate 8 is in contact with the plain bearing 10c of the lug member 10, the thrust plate 8 rotates the swash plate 11 synchronously. It will be responsible for the compression reaction force without assuming the function to do. For this reason, the link mechanism 12 is not involved in the thrust plate 8, and it is possible to individually respond to requests for weight reduction, improvement of torque fluctuation sound, etc. mainly by changing the material of the thrust plate 8.

  Further, in this compressor, since the thrust plate 8 is loosely fitted to the drive shaft 6, the inclination of the seat surface of the front housing 2 that receives the thrust bearing 5 d and the perpendicularity tolerance between the thrust plate 8 and the drive shaft 6. It is also possible to eliminate vibrations and abnormal noise caused by.

  In this compressor, the swash plate 11 has one swash plate arm 11b, but the lug member 10 does not have a conventional lug arm. The first and second intermediate arms 21 and 22 are fastened while the lug member 10 and the swash plate arm 11b are slidably sandwiched between the lug side pin 23 and the swash plate side pin 24. The first guided surface 21b of the first intermediate arm 21 is guided by the parallel surface 10a of the lug member 10 and the parallel surface 11c of the swash plate arm 11b, and the second guided surface 22b of the second intermediate arm 22 is the lug. It is guided by the parallel surface 10a of the member 10 and the parallel surface 11c of the swash plate arm 11b. Thus, in this compressor, no noise is generated and the link mechanism 12 operates smoothly. In this compressor, the lug member 10, the swash plate arm 11b, and the first and second intermediate arms 21 and 22 can be reduced in machining accuracy of parallel surfaces, and these parts can be selectively assembled. Therefore, the manufacturing cost can be reduced.

  Further, in this compressor, since the first and second intermediate arms 21 and 22 are fastened by the lug side pin 23 and the swash plate side pin 24 to form an integrated intermediate arm 20, the first and second intermediate arms 21, The 22 does not move individually, and the first and second intermediate arms 21 and 22 and the swash plate 11 are not easily distorted and twisted from the normal position. Moreover, in this compressor, since it is not necessary to form a lug arm in the lug member 10, manufacture of the lug member 10 and by extension, manufacture of the whole compressor is also easy.

  Further, in this compressor, since there is one swash plate arm 11b, and this swash plate arm 11b is formed so as to avoid the vertical top of the shoe sliding surface 11a, the swash plate 11 is made as an integral part, and the shoe The sliding surface 11a can be easily processed. This is an advantageous effect for the compressor described in, for example, Japanese Patent Application Laid-Open No. 2005-299516.

  The compressor of the second embodiment employs a thrust plate 28 and an elastic member 29 shown in FIG.

  A boss 28c is formed on the thrust plate 28 concentrically with the drive shaft 6, and the inner surface of the boss 28c is a cylindrical inner peripheral surface 28b. A plurality of first convex portions 28d extending on the outer peripheral surface side of the drive shaft 6 are formed on the inner peripheral surface 28b at equal angular intervals. Each of the first convex portions 28d has a plate shape in which the circumferential direction of the drive shaft 6 is thick.

  An elastic member 29 is inserted between the inner peripheral surface 28 b of the thrust plate 28 and the outer peripheral surface of the drive shaft 6. The elastic member 29 includes a main body 29a provided on the outer peripheral surface of the drive shaft 6, and a rubber 29b formed integrally with the main body 29a. In the main body 29a, a plurality of second convex portions 29c extending toward the inner peripheral surface 28b of the thrust plate 28 are formed at equal angular intervals. Each of the second convex portions 29c has a plate shape in which the circumferential direction of the drive shaft 6 is thick. The rubber 29b is formed with a concave portion 29d for accommodating each first convex portion 28d.

  Other configurations are the same as those of the first embodiment. In this compressor, the spring constant of the elastic member 29 can be increased by the first and second convex portions 28d and 29c. Other functions and effects are the same as those of the first embodiment.

  The compressor of the third embodiment employs an electromagnetic clutch 60 instead of the pulley 50 as shown in FIG.

  The electromagnetic clutch 60 includes a rotor 62 rotatably supported on the front housing 2 via a bearing 61, a hub 63 screwed to the drive shaft 61 to transmit the rotation of the rotor 62 to the drive shaft, and a plate on the hub 63. The armature 65 is supported by a spring 64 and the electromagnetic coil 66 is supported by the front housing 2. The leaf spring 64 can be bent in the axial direction by the hub 63 and the armature 65, but cannot be bent in the circumferential direction of the drive shaft 6, and therefore does not become a damper portion.

  Other configurations are the same as those of the first embodiment, and the same configurations are denoted by the same reference numerals and detailed description thereof is omitted. In this compressor, the electromagnetic clutch 60 directly drives the drive shaft 6 via the leaf spring 64, and the transmission performance of the average torque is enhanced. Other functions and effects are the same as those of the first embodiment.

  In the above, the present invention has been described with reference to the first to third embodiments. However, the present invention is not limited to the first to third embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  The present invention is applicable to a vehicle air conditioner.

It is a longitudinal cross-sectional view of the compressor of Example 1. 1 is a schematic longitudinal sectional view of a link mechanism according to a compressor of Example 1. FIG. FIG. 3 is a plan view illustrating a partial cross section of a thrust plate and an elastic member according to the compressor of the first embodiment. 1 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 1. FIG. It is a top view which concerns on the compressor of Example 2 and shows the partial cross section of a thrust plate and an elastic member. 4 is a longitudinal sectional view of a compressor according to Embodiment 3. FIG.

Explanation of symbols

7 ... Crank chamber 1b ... Cylinder bore 1, 2, 4 ... Housing (1 ... Cylinder block, 2 ... Front housing, 4 ... Rear housing)
6 ... Drive shaft 10 ... Lug member 11 ... Swash plate 12 ... Link mechanism 13 ... Piston 11a, 13a, 14 ... Motion conversion mechanism (11a ... Shoe sliding surface, 13a ... Shoe receiving surface, 14 ... Shoe)
9, 29 ... elastic member 8, 28 ... mass body (thrust plate)
5d: Thrust bearing 8f: Weight part 10c: Bearing (plain bearing)
8b, 28b ... inner peripheral surface 28d ... first convex part 29c ... second convex part 29b ... elastic body (rubber)
11b ... swash plate arm P ... virtual plane A1 ... lug side axis A2 ... swash plate side axis 20 ... intermediate arm 21 ... first intermediate arm 22 ... second intermediate arm 53 ... rotor 51 ... hub 50, 60 ... pulley (60 ... Electromagnetic clutch)
52 ... Damper part (damper member)

Claims (13)

A housing forming a crank chamber and a plurality of cylinder bores; a drive shaft having one end projecting from the housing and rotatably supported by the housing in the crank chamber; and a lug rotating synchronously with the drive shaft in the crank chamber A member, a swash plate supported by the drive shaft in the crank chamber so as to be capable of changing the inclination angle, and provided between the lug member and the swash plate in the crank chamber, and changing the inclination angle of the swash plate to the drive shaft. A link mechanism that prevents the swash plate from rotating relative to the drive shaft while allowing the swash plate to reciprocate in each cylinder bore, and the swash plate and each of the swash plate in the crank chamber. A motion conversion mechanism that is provided between the pistons and converts the swinging motion of the swash plate into the reciprocating motion of the pistons;
A variable displacement swash plate compressor, wherein the drive shaft in the crank chamber is provided with a mass body via an elastic member. The crank chamber is provided with a thrust plate that is clearance-fitted to the drive shaft and receives a thrust load, and a thrust bearing provided between the thrust plate and the housing,
The variable capacity swash plate compressor according to claim 1, wherein the mass body is the thrust plate.   3. The variable displacement swash plate compressor according to claim 2, wherein the thrust plate has a weight portion for balancing the rotation.   4. The variable displacement swash plate compressor according to claim 2, wherein a bearing is provided between the thrust plate and the lug member.   5. The variable displacement swash plate compressor according to claim 2, wherein the thrust plate is made of a vibration-proof alloy.   6. The variable displacement swash plate compression according to claim 2, wherein the thrust plate has an inner peripheral surface, and the elastic member is fixed to the inner peripheral surface and the outer peripheral surface of the drive shaft. Machine.   7. The variable capacity swash plate compressor according to claim 6, wherein the elastic member is rubber. The inner peripheral surface is provided with a first convex portion extending toward the outer peripheral surface side, and the outer peripheral surface is provided with a second convex portion extending toward the inner peripheral surface side,
The said elastic member is provided between this 1st convex part and this 2nd convex part, and has an elastic body which has urging | biasing force in the direction which distances and approaches the 1st convex part and this 2nd convex part. The capacity variable swash plate compressor described.   The link mechanism is provided between the lug member, one swash plate arm projecting from the swash plate side to the lug member side, the lug member and the swash plate arm, and the center of the drive shaft The swash plate is supported by the lug member around the lug side axis perpendicular to the virtual plane determined by the axis and the top dead center position of the swash plate, and around the swash plate side axis parallel to the lug side axis. The variable displacement swash plate compressor according to any one of claims 1 to 8, further comprising an intermediate arm pivotally supported by the arm. The intermediate arm has a first intermediate arm extending from the lug member side to the swash plate side, and a second intermediate arm extending from the lug member side to the swash plate side,
The first intermediate arm and the second intermediate arm are pivotally supported on the lug member and the swash plate arm by a lug side pin constituting the lug side axis and a swash plate side pin constituting the swash plate side axis, The variable displacement swash plate compressor according to claim 9, wherein the lug member and the swash plate arm are slidably sandwiched between the lug side pin and the swash plate side pin. The motion conversion mechanism is provided between a shoe sliding surface formed on the front and rear outer peripheral surfaces of the swash plate, a shoe receiving surface formed on each piston, and between the shoe sliding surface and the shoe receiving surface. With a hemispherical shoe
The variable displacement swash plate compressor according to claim 9 or 10, wherein the swash plate arm is formed so as to avoid being vertically above the sliding surface of the shoe. A pulley having a rotor rotatably supported on the housing via a bearing and a hub coupled to the drive shaft and transmitting the rotation of the rotor to the drive shaft is mounted on the housing.
12. The variable displacement swash plate compressor according to claim 1, wherein the pulley has a damper portion between the rotor and the hub. A pulley having a rotor rotatably supported on the housing via a bearing and a hub coupled to the drive shaft and transmitting the rotation of the rotor to the drive shaft is mounted on the housing.
12. The variable displacement swash plate compressor according to claim 1, wherein the pulley does not have a damper portion between the rotor and the hub.

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