JP2009103118A - Capacity-variable type swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a capacity-variable type swash plate compressor in which the preferable operability of a link mechanism and reduction of manufacturing cost are realized. <P>SOLUTION: In this compressor, a link mechanism 12 includes one swash plate arm 11b and intermediate arms 20. The intermediate arms 20 include first and second intermediate arms 21, 22. The first and second intermediate arms 21, 22 are joined while being rotatably supported by a lug member 10 and the swash plate arm 11b via a lug-side pin 23 which constitutes a lug-side axis A1 and a swash-plate-side pin 24 which constitutes a swash-plate-side axis A2 and clamping the lug member 10 and the swash plate arm 11b via the lug-side pin 23 and the swash-plate-side pin 24 so as to allow a sliding movement. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

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

  Conventionally, a capacity variable swash plate compressor disclosed in Patent Document 1 is known. In this compressor, a housing is constituted by a cylinder block, a front housing, and a rear housing, and a plurality of cylinder bores are provided through the cylinder block. The rear housing is formed with a suction chamber and a discharge chamber that communicate with each cylinder bore via a valve unit. A crank chamber is formed by the front housing and the cylinder block, and a drive shaft is rotatably supported by the front housing and the cylinder block. A lug plate is fixed to the drive shaft in the crank chamber, and a thrust bearing is provided between the lug plate and the front housing.

  In the crank chamber, a swash plate is supported on the drive shaft so that the tilt angle can be varied, and a link mechanism is provided between the lug plate and the swash plate. As shown in FIG. 37, this link mechanism is integrated with the lug plate 91, and is integrated with the first and second lug arms 91a and 91b protruding to the swash plate 92 side, and the swash plate 92, on the lug plate 91 side. One protruding swash plate arm 92a, a first intermediate arm 93 provided between the first lug arm 91a and the swash plate arm 92a, and provided between the second lug arm 91b and the swash plate arm 92a. A second intermediate arm 94.

  The first and second intermediate arms 93 and 94 are pivotally supported by the first and second lug arms 91a and 91b with bolts 95, and are pivotally supported by the pin 96 on the swash plate arm 92a. The bolt 95 extends in the direction of the lug side axis A1 orthogonal to the virtual plane P determined by the center axis O of the drive shaft and the top dead center position of the swash plate 92. The pin 96 extends in the direction of the swash plate side axis A2 parallel to the lug side axis A1.

  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. A motion conversion mechanism is provided between the swash plate 92 and each piston. Specifically, this motion conversion mechanism is provided between the swash plate 92 and the oscillating plate between the swash plate 92 and the oscillating plate. And a piston rod that connects the piston to each of the pistons.

  In this compressor, when the swash plate 92 rotates as the drive shaft is driven, each piston reciprocates in the cylinder bore via the swing plate and each piston rod, so that the refrigerant gas flows from the suction chamber into the compression chamber. The refrigerant gas is sucked and compressed, and then discharged into the discharge chamber. During this time, the motion conversion mechanism converts the swing motion of the swash plate 92 into the reciprocating motion of the piston. Further, the link mechanism allows the swash plate 92 to be relatively unrotatable with respect to the drive shaft while allowing the tilt angle fluctuation of the swash plate 92 to the drive shaft.

JP-A-10-176658

  However, in the above-described conventional compressor, the first and second intermediate arms 93 and 94 have guided surfaces 93a, 93b, 94a, and 94b on the front and rear in the rotational direction of the drive shaft, respectively. The guide surfaces 93a and 93b are guided by the inner surface of the first lug arm 91a and one side surface of the swash plate arm 92a, and both guided surfaces 94a and 94b of the second intermediate arm 94 are guided by the inner surface of the second lug arm 91b and the swash plate arm 92a. With other side of the guide. Therefore, in this compressor, both inner surfaces of the first and second lug arms 91a and 91b face each other in parallel, both guided surfaces 93a and 93b of the first intermediate arm 93 are back in parallel, and the second intermediate arm 94 These must be precisely machined so that both guided surfaces 94a, 94b are back in parallel and both side surfaces of the swash plate arm 92a are back in parallel. Otherwise, abnormal noise is generated, the link mechanism does not operate smoothly, capacity controllability is impaired, and durability is impaired due to wear of the link mechanism or the like. For this reason, in this compressor, the effort of manufacturing the components of a link mechanism with high precision or selecting and assembling the components is required, resulting in an increase in manufacturing cost. This problem also applies to the compressor disclosed in Japanese Patent Laid-Open No. 2003-172333 and the compressor disclosed in Japanese Patent Laid-Open No. 2005-299516.

  In the compressor, the first and second intermediate arms 93 and 94 are supported by bolts 95 and pins 96 but are not connected to each other. For this reason, in this compressor, the first and second intermediate arms 93 and 94 have a degree of freedom to move individually, and the first and second intermediate arms 93 and 94 and thus the swash plate 92 are easily distorted and twisted from the normal position. . Also in this case, the link mechanism is worn, and the durability of the compressor is concerned. In this compressor, in order to prevent the first and second intermediate arms 93 and 94 from being twisted, the first and second lug arms 91a and 91b are moved to the swash plate 92 side even at the expense of manufacturing the lug plate 91. Although it protrudes greatly, this is not enough.

  The present invention has been made in view of the above-described conventional situation, and solves the problem of providing a variable displacement swash plate compressor capable of realizing a suitable operability of a link mechanism and a reduction in manufacturing cost. It is an issue that should be done.

A variable displacement swash plate compressor of the present invention includes a housing having a cylinder bore, a drive shaft rotatably supported by the housing, a lug member that rotates in synchronization with the drive shaft in the housing, A swash plate supported on the drive shaft so as to be capable of varying the tilt angle; and provided in the housing between the lug member and the swash plate, and allowing the tilt angle variation of the swash plate to the drive shaft. A link mechanism that prevents the swash plate from rotating relative to the drive shaft, a piston accommodated in the cylinder bore so as to be reciprocally movable, and a swash plate between the piston and the piston. A motion conversion mechanism that converts a dynamic motion into a reciprocating motion of the piston,
The link mechanism includes a swash plate arm protruding from the swash plate toward the lug member, a lug orthogonal to a virtual plane determined by a center axis of the drive shaft and a top dead center position of the swash plate. An intermediate arm pivotally supported by the lug member around a side axis and pivotally supported by the swash plate arm around a swash plate side axis parallel to the lug side axis;
The intermediate arm has a first intermediate arm 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 lug member and the swash plate arm are slidably sandwiched between the lug pin and the swash plate pin so as to be fastened (Claim 1).

  In the compressor of the present invention, the first and second intermediate arms are fastened while the lug member and the swash plate arm are slidably held between the lug side pin and the swash plate side pin. 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, no noise is generated and the link mechanism operates smoothly. Further, in this compressor, the lug member, the swash plate arm, and the first and second intermediate arms can reduce the processing accuracy of the parallel surfaces, and it is necessary to strictly assemble these parts. Therefore, the manufacturing cost can be reduced.

  In the compressor of the present invention, the first and second intermediate arms are fastened together by the lug side pin and the swash plate side pin, so that the first and second intermediate arms do not move individually, The 1 and 2 intermediate arms, and thus the swash plate, are not distorted from their normal positions and are not easily twisted. Moreover, in the compressor of this invention, 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.

  Therefore, the capacity-variable swash plate compressor of the present invention can realize suitable operability of the link mechanism and reduction in manufacturing cost. The suitable operability of the link mechanism leads to the excellent capacity controllability and excellent durability of the compressor.

  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. The width of the lug member is preferably substantially the same as the width of the swash plate arm.

  When the lug member is integral with the drive shaft, a part of the drive shaft can be used as the lug member. The lug member integral with the drive shaft is a portion having an insertion hole for inserting the lug side pin and a press fit hole for press-fitting the lug side pin when the lug side pin and the drive shaft are separate. The lug member integral with the drive shaft may have the same diameter as an adjacent portion of the drive shaft, or may have a different shape such as a large diameter. When the lug member integrated with the drive shaft is employed, the management of the press-fitting allowance when the lug member is press-fitted into the drive shaft can be omitted, and the number of parts can be reduced.

  When the lug member is separate from the drive shaft, the lug member can be fixed to the drive shaft by press fitting or the like. When the lug side pin and the drive shaft are separate bodies, the lug member that is a separate body from the drive shaft has an insertion hole through which the lug side pin is inserted and a press-fit hole into which the lug side pin is press-fitted. When a lug member separate from the drive shaft is employed, the productivity of the drive shaft is improved.

  For the fastening of the first and second intermediate arms by the lug side pin and the fastening of the first and second intermediate arms by the swash plate side pin, means such as press fitting and welding can be adopted.

  The lug-side pin is press-fitted into the first intermediate arm and the second intermediate arm while being loosely fitted to the lug member, and the swash plate-side pin is press-fitted into the first intermediate arm and the second intermediate arm while being loosely fitted to the swash plate arm. (Claim 2).

  In this case, the link mechanism can be assembled as follows.

  First, a lug member and a swash plate arm are prepared. An insertion hole having a slightly larger diameter than the lug side pin is formed in the lug member, and an insertion hole having a slightly larger diameter than the swash plate side pin is formed in the swash plate arm. The first and second intermediate arms are formed with a press-fitting hole having a press-fitting allowance for the lug-side pin and a press-fitting hole having a press-fitting allowance for the swash plate side pin.

  Then, the lug-side pin and the swash plate-side pin are press-fitted into each press-fitting hole of the first intermediate arm, and in this state, the lug-side pin and the swash plate-side pin are inserted into the insertion holes of the lug member and the swash plate arm. The side pin and the swash plate side pin are press-fitted into the press-fitting hole of the second intermediate arm. When the first and second intermediate arms sandwich the lug member or the swash plate arm, the press-fitting is finished. Thus, the first and second intermediate arms are fastened to each other while the dimensional tolerance between the lug member and the swash plate arm is reduced and preferably guided. Further, it is not necessary to prevent the lug side pin and the swash plate side pin from coming off. As a result, high productivity can be exhibited.

  At this time, since the first intermediate arm comes into contact with the lug member and the swash plate arm at a high pressure, an organic liquid such as grease is applied between the first intermediate arm and the lug member and the swash plate arm. It is preferable to prevent them from sticking. The organic liquid can secure a minute gap between the first intermediate arm, the lug member, and the swash plate arm, and it is easy to remove the organic liquid by heating after assembly. It is also possible to first press the lug side pin and the swash plate side pin into each press fitting hole of the second intermediate arm, and press the lug side pin and the swash plate side pin into the press fitting hole of the first intermediate arm in this state. It is.

  Also, the lug side pin and the swash plate side pin have the same diameter, the lug side pin insertion hole and the swash plate side pin insertion hole have the same diameter, the lug side pin press-fitting hole and the swash plate side pin If the press-fitting hole has the same diameter, higher productivity can be exhibited. Not providing the first and second intermediate arms with front / rear and front / back also leads to high productivity.

  In the compressor of the present invention, it is preferable that the swash plate side axis is located on the top dead center side of the swash plate, and the lug side axis is closer to the drive shaft than the swash plate side axis.

  If the intermediate arm is pivotally supported in this way, the link mechanism approaches the drive shaft, so that it is difficult to stir the lubricating oil in the crank chamber and the lubricating oil is difficult to be heated. For this reason, the viscosity of lubricating oil is hard to fall and high slidability can be ensured. Further, the heat of the lubricating oil hardly causes deterioration of the rubber material such as the seal member, and high durability can be exhibited. The top dead center side of the swash plate means a half-circumferential portion of the swash plate including the top dead center position of the swash plate.

  Further, if the intermediate arm is pivotally supported in this way, the center of gravity of the intermediate arm is low and the centrifugal force is also small, so the load in the direction of increasing the inclination angle of the swash plate is reduced at high speed, and the inclination angle of the swash plate can be easily controlled. become. Further, the thrust load acting from the swash plate acts near the drive shaft, and noise and abnormal noise are reduced.

  When the lug side axis is closer to the drive shaft than the swash plate side axis, the lug side axis may intersect the center axis of the drive shaft or be located on the top dead center side of the swash plate. The swash plate is preferably located on the bottom dead center side.

  This also makes it easier to balance the rotation of the sub-assembly consisting of the drive shaft (lug member), link mechanism, swash plate, etc., so that no weight portion is required for the lug member or the weight portion of the lug member is made smaller. It is possible to reduce the weight and reduce the number of processing steps. The bottom dead center side of the swash plate refers to a half circumference portion of the swash plate including the bottom dead center position of the swash plate.

  In the compressor of the present invention, a thrust plate that rotates synchronously with the drive shaft and a thrust bearing provided between the thrust plate and the housing can be provided in the housing. In this case, both the thrust plate and the lug member may constitute an integral lug plate that rotates synchronously with the drive shaft.

  Such a lug plate can be obtained by relatively easily improving a lug plate having a lug arm that has been conventionally used, and thus contributes to a reduction in the manufacturing cost of the compressor of the present invention.

  Such a lug plate may be provided with a support portion that supports at least one anti-swash plate side of the first intermediate arm and the second intermediate arm when the swash plate has a maximum inclination angle. By receiving a compression reaction force transmitted from the piston to the swash plate by the support portion of the lug plate, the link mechanism can be prevented from being deformed and excellent durability can be exhibited. In this lug plate, it is preferable that the support portion is located on the top dead center side of the swash plate.

  Since the compression reaction force acts as a large load on the top dead center side, if the large load is applied to the support portion on the top dead center side, the intermediate arm can be downsized and have excellent durability.

  By the way, the link mechanism requires a reduction in weight, improves torque fluctuation noise due to an increase in inertial mass, and protects the torque limiter due to torque fluctuation when a clutchless type compressor is connected to an engine with large torque fluctuation. Therefore, contradictory properties such as reduction of inertia mass are required. 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.

  In this regard, in the compressor of the present invention, when the thrust plate that rotates synchronously with the drive shaft and the thrust bearing provided between the thrust plate and the housing are provided in the housing, the thrust plate is a lug member or an intermediate arm. It is preferable that it is in contact with (Claim 7).

  That is, it is preferable that the thrust plate and the lug member are separated. In this case, whether the thrust plate is fixed to the drive shaft by press-fitting or the like, or is loosely fitted to the drive shaft, the above requirements can be individually answered by simply changing the material of the thrust plate. Is possible.

  That is, if the lug side axis is located on the bottom dead center side of the swash plate, the swash plate side axis is located on the top dead center side of the swash plate, and the thrust plate and lug member are separated, the drive Since the rotation balance of the sub assembly consisting of the shaft, thrust plate, lug member, link mechanism, swash plate, etc. is good, it is possible not to provide the weight portion on the thrust plate, and to reduce the weight portion provided on the thrust plate. Is possible. Further, if the thrust plate and the lug member are made separate and the thrust plate is in contact with the lug member or the intermediate arm, the thrust plate does not bear the function of rotating the swash plate synchronously. For this reason, the link mechanism is not involved in the thrust plate, and the strength and hardness of the sliding portion essential to the link mechanism are not required for the thrust plate. For these reasons, it is possible to change only the material of the thrust plate in the same shape with respect to the above requirements.

  For example, if the compressor is required to be quiet, such as when the compressor is used in an air conditioner for a high-class vehicle, the thrust plate absorbs the torque fluctuations of the compressor, so the thrust plate is made of iron-based metal or copper-based metal. A large material such as a material having a large mass. On the other hand, if the compressor is required to be lightweight, such as when the compressor is used in an air conditioner for a relatively small vehicle, the thrust plate is made of a small material such as an aluminum-based metal. In addition, when the compressor is connected to an engine with a large torque fluctuation in a clutchless type, the torsional torque acting on the power transmission section between the engine and the compressor becomes excessive. Lightweight, reduce torsional torque and protect torque limiter.

  In the case where the thrust plate and the lug member are separate, it is preferable that the thrust plate is loosely fitted to the drive shaft.

  In this case, it is also possible to eliminate vibration and noise due to the inclination of the seating surface of the housing that receives the thrust bearing and the tolerance of the perpendicularity between the thrust plate and the drive shaft.

  Further, since the compression reaction force acts at a position eccentric from the drive shaft, when the thrust plate is fixed to the drive shaft, a thrust bearing having a large load capacity that can withstand one piece must be employed. In this case, not only the manufacturing cost of the compressor increases, but also the size of the compressor increases due to the increase in the diameter of the thrust bearing. In this regard, when the thrust plate is clearance-fitted to the drive shaft, the thrust plate tilts itself by the compression reaction force, and the thrust bearing does not hit one side. For this reason, it is possible to employ a thrust bearing with a small load capacity, and it is possible to reduce the diameter of the thrust plate, thereby realizing a reduction in the manufacturing cost of the compressor and a reduction in the size of the compressor. When the thrust plate is fitted to the drive shaft, the radial load that supports the drive shaft on the housing can receive a moment acting on the swash plate, so the thrust load is almost at the center of the thrust plate. It is possible to reduce vibration and noise generated from the bearing. If the diameter of the thrust plate and the thrust bearing can be reduced, it is difficult to stir the lubricating oil in the crank chamber and it is possible to suppress the heat generation of the lubricating oil.

  In addition, when a thrust plate fitted with a clearance to the drive shaft is used, and a lug member integrated with the drive shaft is used, the sub-assembly is attached by the drive shaft (lug member), thrust plate, link mechanism, swash plate, etc. It is possible to save the trouble of processing the bearing surface of the thrust plate after assembling.

  In order to fit the thrust plate with the drive shaft while allowing the thrust plate to rotate synchronously with the drive shaft, the thrust plate and the drive shaft can be fitted with a spline or key. In this case, if the sub-assembly is assembled, the thrust plate may be fixed to the drive shaft with a circlip or the like. Even if the drive shaft and the thrust plate are not spline-fitted, if the lug member comes into contact with the thrust plate due to the thrust load transmitted through the piston or the like, the thrust plate rotates synchronously with the drive shaft.

  The thrust plate is preferably made of a vibration-proof alloy (claim 9).

  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. Is 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.

  A lug member separate from the thrust plate may be provided with a support portion that supports at least one anti-swash plate side of the first intermediate arm and the second intermediate arm when the swash plate is at the maximum tilt angle. A compression reaction force transmitted from the piston to the swash plate by the support portion of the lug member is received by the thrust plate, and deformation of the link mechanism can be prevented to exhibit excellent durability. Also in this lug member, it is preferable that the support part is located on the top dead center side of the swash plate.

  Since the compression reaction force acts as a large load on the top dead center side, if the large load is applied to the support portion on the top dead center side, the intermediate arm can be downsized and have excellent durability.

  When a thrust plate fitted with a clearance to the drive shaft is employed, it is preferable that the thrust plate has a side wall having a guide surface for guiding the outer surface of the first intermediate arm and the outer surface of the second intermediate arm ( Claim 11).

  As long as both guide surfaces of both side walls are formed with high accuracy, it is possible to eliminate vibrations and noises regardless of the positional relationship between the thrust plate and the drive shaft or lug member, and tolerances such as symmetry. Further, since the side wall of the thrust plate can reinforce the first and second intermediate arms, the thickness of the first and second intermediate arms can be reduced, and the weight of the link mechanism can be reduced and the rotation balance can be improved. Furthermore, the fixing by press-fitting the lug side pin or swash plate side pin and the first and second intermediate arms is not necessarily required, and the assembling property is improved.

  The intermediate arm can have a weight portion on the bottom dead center side of the swash plate.

  Thereby, a rotation balance can be maintained. It is preferable that the weight portion is not so far away from the drive shaft in the radially outward direction so as not to stir the lubricating oil in the crank chamber so much.

  Between the lug member and the intermediate arm, between the thrust plate and the intermediate arm, or between the intermediate arm and the swash plate arm, a spring having a biasing force that biases in a direction to reduce the inclination angle of the swash plate is provided. (Claim 13).

  In this case, the spring urges the swash plate in a direction in which the inclination angle becomes smaller, and it becomes possible to reduce the torque at the time of startup. In a general compressor, a coil spring positioned between the lug plate and the swash plate is provided around the drive shaft as a spring for biasing the swash plate in such a direction that the inclination angle becomes small. However, when such a coil spring is employed in the compressor of the present invention, it is difficult to position the lug side axis on the bottom dead center side of the swash plate. In this regard, if a spring is provided between the lug member and the intermediate arm, between the thrust plate and the intermediate arm, or between the intermediate arm and the swash plate arm, the lug side axis is positioned on the bottom dead center side of the swash plate. It becomes easy to make it. As such a spring, a leaf spring, a torsion coil spring, or the like can be employed.

  It is preferable that at least one of the lug member and the swash plate arm is formed with an escape portion that avoids twisting by the first intermediate arm and the second intermediate arm.

  In the compressor of the present invention, since the first and second intermediate arms are integrated, it is difficult to twist in the first place. Even if there is a risk of slight kinking due to stacking of tolerances, etc., if at least one of the lug member and the swash plate arm has a relief portion, kinking by the first and second intermediate arms can be avoided. . Further, at least one of the lug member and the swash plate arm is slightly reduced in weight by the escape portion, and it is easy to maintain the rotational balance.

  The gap between the lug member and the lug-side pin is preferably smaller than the gap between the first intermediate arm and the second intermediate arm and the lug member (claim 15).

  In this case, the torque transmitted from the lug member is suitably received by the lug-side pin, and the first and second intermediate arms are unlikely to hit the edge of the lug member at the corners. Thereby, twisting can be further prevented.

  The gap between the swash plate arm and the swash plate side pin is preferably smaller than the gap between the first intermediate arm and the second intermediate arm and the swash plate arm.

  In this case, the moment transmitted from the swash plate is received by the swash plate side pin, and the first and second intermediate arms do not easily hit the edge and corner of the swash plate arm. Thereby, twisting can be further prevented.

  One of the lug side pin and the swash plate side pin and the first intermediate arm may be integrated, and the other of the lug side pin and the swash plate side pin and the second intermediate arm may be integrated (claims). Item 17).

  In this case, a member in which one of the lug side pin and the swash plate side pin is integrated with the first intermediate arm, and the other of the lug side pin and the swash plate side pin and the second intermediate arm are integrated. A sub-assembly is obtained by assembling the member together with the drive shaft, lug member, swash plate and the like. As a result, the number of parts can be reduced, the number of press-fitting operations can be reduced, and the manufacturing cost can be reduced. Further, the lug side pin and the swash plate side pin have the same diameter and the same length, and the first intermediate arm and the second intermediate arm are not different from each other in the front and rear, so that the lug side pin and the swash plate side pin A member in which one of the first intermediate arm and the second intermediate arm is integrated with a member in which the other of the lug-side pin and the swash plate-side pin and the second intermediate arm are integrated is only a member in which the pin and the arm are integrated. Consists of.

  The lug-side pin and the swash plate-side pin may be integrated with one of the first intermediate arm and the second intermediate arm (claim 18).

  In this case, a member in which the lug side pin and the swash plate side pin are integrated with one of the first intermediate arm and the second intermediate arm, and the other of the first intermediate arm and the second intermediate arm are connected to the drive shaft and the lug member. And a sub-assembly is obtained by assembling together with a swash plate or the like. As a result, the number of parts can be reduced, the number of press-fitting operations can be reduced, and the manufacturing cost can be reduced. Further, the lug-side pin and the swash plate-side pin have the same diameter and the same length, and the first intermediate arm and the second intermediate arm are not different in the front and rear, A member in which one of the first intermediate arm and the second intermediate arm is integrated is easily assembled.

  The drive shaft, the lug member, the lug side pin, and at least one of the swash plate, the swash plate arm, and the swash plate side pin can be integrated (claim 19). That is, the drive shaft, the lug member, and the lug side pin may be integrated, or the swash plate, the swash plate arm, and the swash plate side pin may be integrated.

  If the drive shaft, lug member and lug side pin are integrated, the drive shaft, lug member and lug side pin are integrated, the first and second intermediate arms, the swash plate, the swash plate side pin, etc. Subassembly is obtained by assembling. If the swash plate arm and the swash plate side pin are integrated, the member in which the swash plate arm and the swash plate side pin are integrated, the first and second intermediate arms, the drive shaft, the lug side member, and the lug side A sub-assembly can be obtained by assembling pins and the like. As a result, the number of parts can be reduced, the number of press-fitting operations can be reduced, and the manufacturing cost can be reduced.

  A washer is preferably provided between the lug member and the thrust plate.

  In this case, even if the lug member and the thrust plate cause relative rotation, it is possible to prevent wear of both. If the washer is made of an anti-vibration alloy, noise and vibration can be reduced. It is also possible to form a support portion for defining the maximum inclination angle of the swash plate on the swash plate so that the support portion contacts the washer.

  In addition, the lug member is preferably formed of an iron-based material in the same manner as the drive shaft in order to rotate synchronously with the drive shaft and transmit torque to the swash plate via the link mechanism. On the other hand, the thrust plate may be formed of an aluminum-based material for weight reduction or the like. In this combination, the washer between the lug member and the thrust plate can effectively prevent the wear of the thrust plate.

  The lug side pin is loosely fitted to the first intermediate arm and the second intermediate arm while being press-fitted into the lug member, and the swash plate side pin is loosely fitted to the first intermediate arm and the second intermediate arm while being press-fitted into the swash plate arm, It is also preferable that the first intermediate arm and the second intermediate arm are secured from the lug side pin and the swash plate side pin (claim 21).

  In this case, the link mechanism can be assembled as follows.

  First, a lug member and a swash plate arm are prepared. The lug member is formed with a press-fitting hole having a press-fitting allowance for the lug-side pin, and the swash plate arm is formed with a press-fitting hole having a press-fitting allowance for the swash plate side pin. In addition, the first and second intermediate arms are formed with an insertion hole having a slightly larger diameter than the lug side pin and an insertion hole having a slightly larger diameter than the swash plate side pin.

  Then, the lug side pin and the swash plate side pin are press-fitted into the press fitting holes of the lug member and the swash plate arm, and the lug side pin and the swash plate side pin are inserted into the insertion holes of the first intermediate arm and the second intermediate arm in this state. While slipping through, secure it. A side wall, a circlip, or the like can be used as the stopper. Thus, the first and second intermediate arms are fastened to each other while the dimensional tolerance between the lug member and the swash plate arm is reduced and preferably guided.

  When loosely fitting the lug side pin and the swash plate side pin and the first and second intermediate arms, a thrust plate that rotates synchronously with the drive shaft, and a thrust bearing provided between the thrust plate and the housing are provided in the housing. Can be provided. Preferably, at least one of the thrust plate and the swash plate is formed with a side wall having a guide surface for guiding the outer surface of the first intermediate arm and the outer surface of the second intermediate arm.

  In this case, even if the moment acting on the swash plate is large, the lug side pin and the first and second intermediate arms loosely fitted to the swash plate side pin can stably transmit the thrust load from the swash plate arm to the lug member. Further, since the side wall of the thrust plate can reinforce the first and second intermediate arms, the thickness of the first and second intermediate arms can be reduced, and the weight of the link mechanism can be reduced and the rotation balance can be improved.

  Further, when the lug side pin and the swash plate side pin and the first and second intermediate arms are loosely fitted, the first and second intermediate arms rotate around one of the lug side pin and the swash plate side pin in the rotational direction of the drive shaft. Is preferably thicker than the thickness around the other (claim 23).

  In this case, in the first and second intermediate arms, one of the lug-side pin and the swash plate-side pin is loosely fitted with a longer length than the other, and the first and second intermediate arms are not easily inclined in the rotation direction of the swash plate. Become. For this reason, it is difficult for the first and second intermediate arms to come off from the lug-side pin and the swash plate-side pin, and the link mechanism has less backlash and stable operability. For this reason, noise and abnormal noise are reduced in the compressor.

  When the lug side pin is loosely fitted to the lug member and the swash plate side pin is loosely fitted to the swash plate arm, there is at least one between the lug member and the lug side pin and between the swash plate arm and the swash plate side pin. A bearing is preferably provided (claim 24).

  In this case, the slidability of at least one of the lug member and the lug side pin and between the swash plate arm and the swash plate side pin is improved, and the operability and quietness of the link mechanism are improved.

  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 the piston, and a hemispherical shoe provided between the shoe sliding surface and the shoe receiving surface. It can consist of In this case, it is preferable that the swash plate arm is formed so as to avoid the vertical direction of the shoe sliding surface.

  In this case, the swash plate can easily process the shoe sliding surface, and the productivity is improved.

  Hereinafter, Embodiments 1 to 26 embodying the present invention will be described 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, a lug plate 8 is fixed to the drive shaft 6. 2-4, the lug plate 8 is formed with a press-fitting hole 8a, and the drive shaft 6 is press-fitted into the press-fitting hole 8a. The lug plate 8 includes a thrust plate 9 and a lug member 10 that are integrally formed. Since this lug plate 8 is obtained by improving the lug plate with the lug arm used conventionally relatively easily, it contributes to the reduction of the manufacturing cost of the compressor.

  The thrust plate 9 is formed in a disc shape, and a thrust bearing 5 d is provided between the thrust plate 9 and the front housing 2. On the outer periphery on the top dead center side of the thrust plate 9, a weight portion 9a is formed as shown in FIG.

  The lug member 10 is formed in a horseshoe shape having parallel surfaces 10a extending back and parallel to each other on the bottom dead center side. Further, as shown in FIG. 4, an insertion hole 10 b orthogonal to both parallel surfaces 10 a is provided on the bottom dead center side of the lug member 10. The insertion hole 10b has 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 plate 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. As shown in FIGS. 2 and 3, one support portion 11 e protrudes from the bottom dead center side of the surface of the swash plate 11 on the lug member 10 side toward the lug member 10, and the support portion 11 e corresponds to the swash plate 11. Is in contact with the rear surface of the lug member 10 at the maximum tilt angle.

  As shown in FIG. 1, a plurality of cylinder bores 1 b extending in the axial direction are concentrically provided in the cylinder block 1. 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.

  A biasing spring 27 that biases the swash plate 11 is provided between the lug member 10 and the swash plate 11 so as to reduce the inclination angle. Further, a circlip 28a is provided at the rear of the drive shaft 6, and a return spring 28b for biasing the swash plate 11 is provided at the front of the circlip 28a so as to increase the inclination angle.

  A rear chamber 1c is formed at the rear end of the cylinder block 1 coaxially with the shaft hole 1a. In the rear chamber 1 c, a thrust bearing 29 a is provided at the rear end of the drive shaft 6, and a pressing spring 29 b is provided between the thrust bearing 29 a and the valve unit 3. The urging spring 27, the return spring 28b, and the pressing spring 29b are coil springs.

  The rear housing 4 is formed with a suction chamber 4a and a discharge chamber 4b. 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.

  2 to 4, the link mechanism 12 is integrated with the swash plate 11, and has a single swash plate arm 11 b that protrudes toward the lug plate 8 on the top dead center side, and the lug member 10 and the swash plate. And an intermediate arm 20 sandwiching the 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, lug side pins 23 and swash plate side pins 24.

  As shown in FIG. 4, the first intermediate arm 21 extends in parallel with a virtual plane P determined by the center axis O of the drive shaft 6 and the top dead center position of the swash plate 9, and makes a pair and backs each other. The outer surface 21 a and the inner surface 21 b are provided before and after the rotational direction R of the drive shaft 6. Further, the second intermediate arm 22 extends parallel to the virtual plane P, and has an outer surface 22 a and an inner surface 22 b that make a pair and back to each other, with the front and rear 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 outer surface 21a and the inner surface 21b, and press-fitting holes 22c at right angles to the outer surface 22a and inner surface 22b at both ends of the second intermediate arm 22. 22d is penetrated. The press-fitting holes 21c and 22c have a press-fitting allowance for a lug-side pin 23 described later, and the press-fitting holes 21d and 22d have a press-fitting allowance for a swash plate side pin 24 described later.

  As shown in FIG. 2, the swash plate arm 11 b is formed to have substantially the same width as between the parallel surfaces 10 a of the lug member 10, and has parallel surfaces 11 c that extend parallel to each other on the back surface. The swash plate arm 11b is provided with an insertion hole 11d perpendicular to both parallel surfaces 11c. The insertion hole 11d is formed to have a slightly larger diameter than a swash plate side pin 24 described later.

  The insertion hole 10b of the lug member 10 and the press-fitting holes 21c and 22c of the first and second intermediate arms 21 and 22 extend in the direction of the lug side axis A1 orthogonal to the virtual plane P, as shown in FIG. Further, 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, the lug-side pin 23 is 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 pin 24 is loosely fitted to the swash plate arm 11b and first and second. The intermediate arms 21 and 22 are press-fitted. 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.

  The above link mechanism 12 is assembled as follows. First, the drive shaft 6, the lug plate 8, the swash plate 11, the first and second intermediate arms 21 and 22, the lug side pin 23, and the swash plate side pin 24 are prepared. The first and second intermediate arms 21 and 22 are the same plate material without front and back and front and back, and the lug side pin 23 and the swash plate side pin 24 are the same pins without different left and right.

  Then, the lug plate 8 is press-fitted into the drive shaft 6, and the drive shaft 6 is inserted through the swash plate 11. Next, the lug-side pin 23 and the swash plate-side pin 24 are press-fitted into the press-fitting holes 21c and 21d of the first intermediate arm 21, and in this state, the lug-side pin 23 and the swash plate-side pin 24 are inserted into the lug member 10 and the swash plate arm. The lug side pin 23 and the swash plate side pin 24 are press-fitted into the press-fitting holes 22 c and 22 d of the second intermediate arm 22 while being inserted into the insertion holes 10 b and 11 d of 11 b.

  At this time, the first and second intermediate arms 21 and 22 are not front and back or front and back, and the lug side pin 23 and the swash plate side pin 24 are the same pin, and the insertion holes 10b and 11d have the same diameter. Since the press-fitting holes 21c, 21d, 22c, and 22d have the same diameter, high productivity is exhibited. Further, since the first intermediate arm 21 comes into contact with the lug member 10 and the swash plate arm 11b with high pressure, grease is applied between the first intermediate arm 21 and the lug member 10 and the swash plate arm 11b. And prevent them from sticking. This is because a small gap can be secured between the first intermediate arm 21, the lug member 10, and the swash plate arm 11b by the grease. Further, a minute gap may be secured by forming a thin film of a coating that easily wears by sliding on the first intermediate arm 21 or the lug member 10 and the swash plate arm 11b in advance. When the first and second intermediate arms 21 and 22 sandwich the lug member 10 or the swash plate arm 11b, the press-fitting is finished.

  Thus, the first and second intermediate arms 21 and 22 are fastened to each other while being suitably guided by reducing the dimensional tolerance between the lug member 10 and the swash plate arm 11b. Further, it is not necessary to prevent the lug side pin 23 and the swash plate side pin 24 from coming off. As a result, high productivity can be exhibited. As described above, the sub-assembly including the drive shaft 6, the lug plate 8, the link mechanism 12, and the swash plate 11 is assembled. After the assembly, the grease is removed by heating, and the link mechanism 12 is obtained. The compressor is assembled by the link mechanism 12.

  In the compressor configured as described above, when the drive shaft 6 is driven in the rotation direction R, the lug plate 8 and the swash plate 9 rotate synchronously, and the piston 13 reciprocates in the cylinder bore 1b via the shoe 14. To do. 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. In particular, in this compressor, since the lug side axis A1 is located on the bottom dead center side of the swash plate 11 and the swash plate side axis A2 is located on the top dead center side of the swash plate 11, it is easy to balance the rotation. Thus, the weight portion is not required for the lug member 11, and the weight is reduced and the number of processing steps is reduced.

  In this compressor, 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 pin 23 and the swash plate pin 24. The inner 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 inner surface 22b of the second intermediate arm 22 is inclined with the parallel surface 10a of the lug member 10. It is guided by the parallel surface 11c of the 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.

  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 distorted from the normal position and are not easily twisted. 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.

  Therefore, this compressor can realize suitable operability of the link mechanism 12 and reduction in manufacturing cost. The suitable operability of the link mechanism 12 leads to excellent capacity controllability and excellent durability in the compressor.

  Moreover, in this compressor, since the intermediate arm 20 is pivotally supported as described above, the link mechanism 12 approaches the drive shaft 6. For this reason, it is difficult to stir the lubricating oil in the crank chamber 7 and the lubricating oil is difficult to be heated. For this reason, the viscosity of lubricating oil is hard to fall and high slidability can be ensured. Further, the heat of the lubricating oil hardly causes deterioration of the rubber material such as the shaft seal device 5c, and high durability can be exhibited. Further, since the intermediate arm 20 is pivotally supported in this way, the center of gravity of the intermediate arm 20 is low and the centrifugal force is also small. Therefore, the load in the direction of increasing the tilt angle of the swash plate 11 at a high speed becomes small, and the swash plate The inclination angle of 11 can be easily controlled.

  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 link mechanism 30 shown in FIGS. 5 and 6. In this link mechanism 30, an outer spline 31a is formed on the drive shaft 31, an inner spline 32a is formed on the thrust plate 32, and the outer spline 31a and the inner spline 32a are fitted. Thus, the thrust plate 32 is loosely fitted to the drive shaft 31.

  The thrust plate 32 is formed of a vibration-proof alloy. The lug member 33 is separate from the thrust plate 32 and is in contact with the thrust plate 32. The lug member 33 is formed with a press-fit hole 33a, and the drive shaft 31 is press-fit into the press-fit hole 33a. Other configurations are the same as those of the first embodiment.

  In this compressor, since the thrust plate 32 and the lug member 33 are separate bodies and the thrust plate 32 is in contact with the lug member 33, the thrust plate 32 does not bear the function of rotating the swash plate 11 synchronously. It will bear the compression reaction force. For this reason, the link mechanism 30 is not involved in the thrust plate 32, and strength and hardness such as between the insertion holes 10 b and 11 d and the lug side pins 23 and the swash plate side pins 24 are not required for the thrust plate 32. . For this reason, it is possible to individually respond to the request for weight reduction and the improvement of the torque fluctuation sound, etc., mainly by changing the material of the thrust plate 32.

  In this compressor, since the thrust plate 32 is loosely fitted to the drive shaft 31, the inclination of the seat surface of the front housing 2 that receives the thrust bearing 5 d and the tolerance of the perpendicularity between the thrust plate 32 and the drive shaft 31. It is also possible to eliminate vibrations and abnormal noise caused by.

  Further, in this compressor, since the thrust plate 32 is loosely fitted to the drive shaft 31, the thrust plate 32 tilts itself by the compression reaction force so that the thrust bearing 5d does not hit one side. For this reason, it is possible to employ the thrust bearing 5d having a small load capacity, the thrust plate 32 can also be reduced in diameter, and a reduction in the manufacturing cost of the compressor and a reduction in the size of the compressor are realized. Further, since the moment acting on the swash plate 11 can be received by the radial bearings 5a and 5b, the thrust load can be received substantially at the center of the thrust plate 32, and vibrations generated from the radial bearings 5a and 5b and the thrust bearing 5d. And noise can be reduced. Further, by reducing the diameter of the thrust plate 32 and the thrust bearing 5d, it is difficult to stir the lubricating oil in the crank chamber 7, and it is possible to suppress the heat generation of the lubricating oil. Other functions and effects are the same as those of the first embodiment.

  The compressor of Example 3 employs a link mechanism 40 shown in FIG. In the link mechanism 40, a part of the drive shaft 41 is a lug member 41a. Other configurations are the same as those of the second embodiment.

  In this compressor, the management of the press-fitting allowance when the lug member 41a is press-fitted into the drive shaft 41 can be omitted. Further, in this compressor, it is possible to save the trouble of processing the seating surface of the thrust plate 32 after assembling the sub-assembly with the drive shaft 41 (lug member 41a), the thrust plate 32, the link mechanism 40, the swash plate 11, and the like. . Other functions and effects are the same as those of the second embodiment.

  The compressor of the fourth embodiment employs a link mechanism 50 shown in FIG. In this link mechanism 50, the swash plate 11 does not have the support portion 11 e, and the support portion 9 b is provided on the thrust plate 9 of the lug plate 8. The support portion 9b protrudes from the top dead center side of the surface on the swash plate 11 side of the thrust plate 9 toward the swash plate 11, and the first and second intermediate arms 21 and 22 when the swash plate 11 is at the maximum tilt angle. This is in contact with the side surface of the thrust plate 9 and supports the anti-swash plate side of the first and second intermediate arms 21 and 22. Other configurations are the same as those of the first embodiment.

  In this compressor, a compression reaction force transmitted from the piston 13 to the swash plate 11 is received by the support portion 9b of the thrust plate 9 integrated with the lug member 10, and the deformation of the link mechanism 50 is prevented and excellent durability is exhibited. can do. In particular, in this compressor, since the lug side axis A1 is located on the bottom dead center side of the swash plate 11 and the swash plate side axis A2 is located on the top dead center side of the swash plate 11, the compression reaction force is It acts as a large load Fu on the top dead center side. For this reason, by receiving a large load Fu at the top dead center side support portion 9b, the first and second intermediate arms 21 and 22 and the swash plate side pin 24 can be reduced in size and excellent in durability. Other functions and effects are the same as those of the first embodiment.

  The compressor of the fifth embodiment employs a link mechanism 60 shown in FIG. In this link mechanism 60, the swash plate 11 does not have the support portion 11 e, and the support portion 34 a is provided on the lug member 34 that is separate from the thrust plate 32. The support portion 34a protrudes laterally at two locations on the top dead center side of the side surface of the lug member 34, and the side surface of the first and second intermediate arms 21 and 22 on the lug member 34 side when the swash plate 11 is at the maximum inclination angle. The first and second intermediate arms 21 and 22 are in contact with each other and support the anti-swash plate side. Other configurations are the same as those in the second and third embodiments.

  In this compressor, the thrust plate 32 is loosely fitted to the drive shaft 31, and the lug member 34 receives a compression reaction force transmitted from the piston 13 to the swash plate 11 by the support portion 34a. Other functions and effects are the same as those of the second and third embodiments.

  The compressor of the sixth embodiment employs a link mechanism 70 shown in FIG. In the link mechanism 70, the first and second intermediate arms 21 and 22 have a weight portion 22e (the weight portion of the first intermediate arm 21 is not shown) on the bottom dead center side of the swash plate 11. Other configurations are the same as those of the second embodiment.

  In this compressor, the rotation balance can be maintained by the weight portions 22 a of the first and second intermediate arms 21 and 22. Other functions and effects are the same as those of the compressor of the second embodiment.

  The compressor of the seventh embodiment employs a link mechanism 80 shown in FIG. In the link mechanism 80, a pair of side walls 35 and 36 extending to the swash plate 11 side are formed on the thrust plate 32 that is separate from the lug member 33. The side walls 35 and 36 protrude until both end faces of the swash plate side pin 24 are partially covered. Inside the side walls 35 and 36, guide surfaces 35a and 36a for guiding the outer surface 21a of the first intermediate arm 21 and the outer surface 22a of the second intermediate arm 22 are formed. Other configurations are the same as those of the second embodiment.

  In this compressor, side walls 35 and 36 are formed on the thrust plate 32 that is loosely fitted to the drive shaft 31. Therefore, if both the guide surfaces 35a and 36a of the side walls 35 and 36 are formed accurately, the thrust plate Irrespective of tolerances such as the positional relationship between the shaft 32 and the drive shaft 31 or the lug member 33 and the degree of symmetry, it is possible to eliminate vibration and noise. Further, since the side walls 35 and 36 of the thrust plate 32 can reinforce the first and second intermediate arms 21 and 22, the plate thickness of the first and second intermediate arms 21 and 22 can be reduced, the weight of the link mechanism 80 can be reduced, and the rotation balance can be reduced. Can be improved. Furthermore, the fixing by press-fitting the lug side pin 23 or the swash plate side pin 24 and the first and second intermediate arms 21 and 22 is not necessarily required, and the assembling property is improved. Other functions and effects are the same as those of the compressor of the second embodiment.

  The first and second intermediate arms are not limited to plate-like ones, and may be rod-like ones. Also, the width of the lug member need not be the same as the width of the swash plate arm. For example, as shown in FIG. 12, the width of the lug member 10 may be larger than the width of the swash plate arm 11b. In this case, as the first and second intermediate arms 25 and 26, bent plate-like or rod-like ones can be adopted.

  In the compressor of the ninth embodiment, as shown in FIG. 13, the lug member 10 and the thrust plate 9 constitute an integral lug plate 8, and the lug plate 8 is press-fitted into the drive shaft 6. A leaf spring 37 is provided between the thrust plate 9 and the second intermediate arm 22. The biasing spring 27 made of the coil spring of the first embodiment shown in FIG. 1 is omitted. The leaf spring 37 has an urging force that urges the swash plate 11 in the direction of decreasing the inclination angle. A leaf spring may be provided between the thrust plate 9 and the first intermediate arm 21. Other configurations are the same as those of the first embodiment.

  In this compressor, the swash plate 11 is urged by the leaf spring 37 in a direction in which the inclination angle becomes smaller, and the torque at the time of activation can be reduced. Further, since the conventional biasing spring 27 can be omitted by adopting the leaf spring 37, the lug-side pin 23 can be easily positioned on the bottom dead center side of the swash plate 11. Other functions and effects are the same as those of the first embodiment.

  In the compressor of Example 10, the lug member 10 and the thrust plate 38 are separated as shown in FIG. Further, an insertion hole 38a is formed through the thrust plate 38, and the drive shaft 6 is inserted through the insertion hole 38a. Thus, the thrust plate 38 is loosely fitted to the drive shaft 6. A leaf spring 37 is provided between the thrust plate 38 and the second intermediate arm 22. The biasing spring 27 made of the coil spring of the first embodiment shown in FIG. 1 is omitted. A leaf spring may be provided between the thrust plate 38 and the first intermediate arm 21. Other configurations are the same as those of the ninth embodiment.

  This compressor can achieve the same effects as those of the ninth embodiment. Although the drive shaft 6 and the thrust plate 38 are not spline-fitted, the lug member 10 is thrust by the thrust load transmitted through the piston 13, the shoe 14, the swash plate 11, the link mechanism 12, and the leaf spring 37. The thrust plate 38 abuts on the plate 38 and rotates synchronously with the drive shaft 6.

  In the compressor of Example 11, a torsion coil spring 39 is provided between the second intermediate arm 22 and the swash plate arm 11b as shown in FIG. The coil portion 39 a of the torsion coil spring 39 is inserted into the swash plate side pin 24, one end 39 b of the torsion coil spring 39 is fixed to the swash plate arm 11 b, and the other end 39 c of the torsion coil spring 39 is fixed to the second intermediate arm 22. Has been. The biasing spring 27 made of the coil spring of the first embodiment shown in FIG. 1 is omitted. A torsion coil spring may be provided between the lug member 10 and the second intermediate arm 22, between the first intermediate arm 21 and the swash plate arm 11 b, or between the lug member 10 and the first intermediate arm 21. . Other configurations are the same as those of the ninth embodiment.

  This compressor can achieve the same effects as those of the ninth embodiment.

  In the compressor of the twelfth embodiment, as shown in FIGS. 16 and 17, a disk-shaped lug member 42 is press-fitted into the drive shaft 6. A thrust bearing 5d that receives a thrust load with the front housing 2 (see FIG. 1) is provided on the front surface of the lug member 42, and a lug arm 42a that protrudes toward the swash plate 11 is provided on the rear surface of the lug member 42. Yes. The lug arm 42 a is located on the top dead center side of the swash plate 11.

  The lug arm 42a has an insertion hole 42b, and the swash plate arm 11b has an insertion hole 11d. The lug side pin 23 is inserted into the insertion hole 42b, and the swash plate side pin 24 is inserted into the insertion hole 11d. The first and second intermediate arms 21 and 22 are pivotally supported on the lug arm 42a and the swash plate arm 11b by the lug side pin 23 and the swash plate side pin 24, and the lug arm 42a by the lug side pin 23 and the swash plate side pin 24. The swash plate arm 11b is slidably clamped and fastened.

  As shown in FIG. 17, escape portions 42 c are formed on both side surfaces of the lug arm 42 a so as to move away from the inner surfaces 21 b and 22 b of the first and second intermediate arms 21 and 22 as the distance from the insertion hole 42 b increases. The swash plate arm 11b is formed with a relief portion 11f so as to be away from the inner surfaces 21b, 22b of the first and second intermediate arms 21, 22 as the distance from the insertion hole 11d increases. In the compressor of the twelfth embodiment, the link mechanism 43 is configured as described above. Other configurations are the same as those of the first embodiment.

  In this compressor, since the first and second intermediate arms 21 and 22 are integrated, it is difficult to twist in the first place. Even if there is a risk of slight twisting due to stacking of tolerances, the lug arm 42a and the swash plate arm 11b are provided with the relief portions 42c and 11f. It can be avoided.

  Further, in this compressor, the lug member 42 and the swash plate 11 are slightly reduced in weight by the escape portions 42c and 11f formed in the lug arm 42a and the swash plate arm 11b, and it is easy to maintain a rotational balance. Other functions and effects are the same as those of the first embodiment.

  In the compressor according to the thirteenth embodiment, as shown in FIGS. 18 and 19, an insertion hole 44a is provided through the thrust plate 44, and the drive shaft 6 is inserted through the insertion hole 44a. Thus, the thrust plate 44 is loosely fitted to the drive shaft 6. A thrust bearing 5d that receives a thrust load with the front housing 2 (see FIG. 1) is provided on the front surface of the thrust plate 44. The drive shaft 6 and the thrust plate 44 are not spline-fitted, but the thrust plate 44 rotates in synchronization with the drive shaft 6. A horseshoe-shaped lug member 45 is press-fitted into the drive shaft 6 behind the thrust plate 44.

  The lug member 45 has an insertion hole 45b, and the swash plate arm 11b has an insertion hole 11d. The lug side pin 23 is inserted through the insertion hole 45b, and the swash plate side pin 24 is inserted through the insertion hole 11d. The first and second intermediate arms 21 and 22 are pivotally supported by the lug member 45 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 45 and the swash plate arm 11b are slidably clamped and fastened.

  As shown in FIG. 19, relief portions 45 c are formed on both side surfaces of the lug member 45 so as to move away from the inner surfaces 21 b, 22 b of the first and second intermediate arms 21, 22 as the distance from the insertion hole 45 b increases. The swash plate arm 11b is formed with a relief portion 11f so as to be away from the inner surfaces 21b, 22b of the first and second intermediate arms 21, 22 as the distance from the insertion hole 11d increases. In the compressor according to the thirteenth embodiment, the link mechanism 46 is configured as described above. Other configurations are the same as those of the tenth embodiment.

  Also in this compressor, the same operation effect as Example 12 can be produced.

  In the compressor of the fourteenth embodiment, as shown in FIGS. 20 and 21, the lug member 47 and the thrust plate 48 constitute an integral lug plate 49, and the lug plate 49 is press-fitted into the drive shaft 6. . The lug member 47 has an insertion hole 47a, and the swash plate arm 11b has an insertion hole 11d.

  In this compressor, two members 51 are used. The member 51 includes a plate-like arm portion 51a and a pin portion 51b extending from the one end of the arm portion 51a at a right angle to the arm portion 51a. A press-fit hole 51c is provided through the other end of the arm portion 51a.

  The arm portion 51a is a portion that can be either the first intermediate arm or the second intermediate arm, and has an outer surface 51d and an inner surface 51e that are paired and back from each other. The pin portion 51 b is a portion that can be either a lug-side pin or a swash plate-side pin, and has a diameter that is press-fitted into the press-fitting hole 51 c of another member 51. In the compressor according to the fourteenth embodiment, the link mechanism 52 is configured as described above. Other configurations are the same as those of the first embodiment.

  In this compressor, a sub-assembly is obtained by assembling the two members 51 together with the drive shaft 6, the lug plate 49, the swash plate 11, and the like. As a result, the number of parts can be reduced, the number of press-fitting operations can be reduced, and the manufacturing cost can be reduced. Other effects can be obtained in the same manner as in the first embodiment.

  As shown in FIGS. 22 and 23, in the compressor according to the fifth embodiment, an insertion hole 53a is inserted through the thrust plate 53, and the drive shaft 6 is inserted through the insertion hole 53a. Thus, the thrust plate 53 is loosely fitted to the drive shaft 6. A thrust bearing 5d that receives a thrust load with the front housing 2 (see FIG. 1) is provided on the front surface of the thrust plate 53. The drive shaft 6 and the thrust plate 53 are not spline-fitted, but the thrust plate 53 rotates in synchronization with the drive shaft 6. A horseshoe-shaped lug member 54 is press-fitted into the drive shaft 6 behind the thrust plate 53. The lug member 54 is provided with an insertion hole 54b. In the compressor according to the fifteenth embodiment, the link mechanism 55 is configured as described above. Other configurations are the same as those in the fourteenth embodiment.

  This compressor can achieve the same effects as those of the fourteenth embodiment.

  In the compressor of the sixteenth embodiment, a member 56 and a plate-like arm 57 are used. The member 56 includes a plate-like arm portion 56a, a first pin portion 56b extending at a right angle from one end of the arm portion 56a to the arm portion 56a, and a right angle from the other end of the arm portion 56a to the arm portion 56a. It consists of the 2nd pin part 56c.

  Press-fitting holes 57 a and 57 b are provided at both ends of the arm 57. The arm 57 has an outer surface 57d and an inner surface 57e that are paired with each other and are back to each other.

  The arm portion 56a is a portion that can be either the first intermediate arm or the second intermediate arm, and has an outer surface 56d and an inner surface 51e that are paired with each other and are back from each other. The first pin portion 56 b is a portion that can be one of a lug-side pin and a swash plate-side pin, and has a diameter that is press-fitted into the press-fit holes 57 a and 57 b of the arm 57. The second pin portion 56 c is a portion that can be the other of the lug-side pin and the swash plate-side pin, and has a diameter that is press-fitted into the press-fit holes 57 a and 57 b of the arm 57. In the compressor according to the sixteenth embodiment, the link mechanism 58 is configured as described above. Other configurations are the same as those of the tenth embodiment.

  In this compressor, the subassembly is obtained by assembling the member 56 and the arm 57 together with the drive shaft 6, the thrust plate 53, the lug member 54, the swash plate 11, and the like. As a result, the number of parts can be reduced, the number of press-fitting operations can be reduced, and the manufacturing cost can be reduced. Other functions and effects are the same as those of the tenth embodiment.

  As shown in FIGS. 25 and 26, in the compressor of the seventeenth embodiment, an insertion hole 59a is formed through the thrust plate 59, and the drive shaft 61 is inserted through the insertion hole 59a. Thus, the thrust plate 59 is loosely fitted to the drive shaft 61.

  On the drive shaft 61, a bulging portion 61a as a lug member is formed with a large diameter behind a portion where the thrust plate 59 is fitted with clearance. Further, pin portions 61b and 61c that are orthogonal to the central axis O and extend in directions away from each other protrude from the bulging portion 61a. In the compressor according to the seventeenth embodiment, the link mechanism 62 is configured as described above. Other configurations are the same as those of the tenth embodiment.

  In this compressor, a sub-assembly is obtained by assembling the drive shaft 61, the first and second intermediate arms 21 and 22, the swash plate 11, the swash plate side pin 24, and the like. As a result, the number of parts can be reduced, the number of press-fitting operations can be reduced, and the manufacturing cost can be reduced. The swash plate 11, the swash plate arm 11b, and the swash plate side pin 24 may be integrated.

  As shown in FIG. 27, the compressor of the eighteenth embodiment has a press-fit hole 63a penetrating through the thrust plate 63, and a drive shaft 61 is press-fit into the press-fit hole 63a. The press-fitting hole 63a is a part of the bulging portion 61a. In the compressor according to the eighteenth embodiment, the link mechanism 64 is configured as described above. Other configurations are the same as those in the seventeenth embodiment.

  In this compressor, the same operational effects as those of the seventeenth embodiment can be obtained. The swash plate 11, the swash plate arm 11b, and the swash plate side pin 24 may be integrated.

  In the compressor of the nineteenth embodiment, as shown in FIG. 28, a lug member 81 press-fitted into the drive shaft 6 is formed in a rectangular parallelepiped shape, and both side surfaces are parallel surfaces 81a extending in parallel with the back surfaces of each other. On the top dead center side of the lug member 81, an insertion hole 81b orthogonal to both parallel surfaces 81a is provided. The insertion hole 81 b is formed to have a slightly larger diameter than the lug side pin 23. Other configurations are the same as those in the eighteenth embodiment.

  When the lug-side pin 23 is separated from the central axis O of the drive shaft 6, the lug member 6 can be separated from the drive shaft 6 and the size of the parts can be avoided. Other functions and effects are the same as those of the eighteenth embodiment.

  In the compressor of the twentieth embodiment, as shown in FIG. 29, a disk-shaped lug member 65 is press-fitted into the drive shaft 6. A thrust bearing 5d that receives a thrust load with the front housing 2 (see FIG. 1) is provided on the front surface of the lug member 65, and a lug arm 65a that protrudes toward the swash plate 11 is provided on the rear surface of the lug member 65. Yes.

  The lug arm 65a has an insertion hole 65b, and the swash plate arm 11b has an insertion hole 11d. The lug side pin 23 is inserted into the insertion hole 65b, and the swash plate side pin 24 is inserted into the insertion hole 11d. The first and second intermediate arms 21 and 22 are pivotally supported on the lug arm 42a and the swash plate arm 11b by the lug side pin 23 and the swash plate side pin 24, and the lug arm 42a by the lug side pin 23 and the swash plate side pin 24. The swash plate arm 11b is slidably clamped and fastened.

  A gap g1 between the insertion hole 65b of the lug arm 65a and the lug-side pin 23 is made smaller than a gap g2 between the first and second intermediate arms 21 and 22 and the lug arm 65a. Further, the gap g1 between the insertion hole 11d of the swash plate arm 11b and the swash plate side pin 24 is made smaller than the gap g2 between the first and second intermediate arms 21 and 22 and the swash plate arm 11b. In the compressor of the twentieth embodiment, the link mechanism 66 is configured as described above. Other configurations are the same as those of the ninth embodiment.

  In this compressor, the torque transmitted from the lug member 65 is preferably received by the lug-side pin 23, and the first and second intermediate arms 21 and 22 are unlikely to hit the edges and corners of the lug member 65. Further, the moment transmitted from the swash plate 11 is received by the swash plate side pin 11b, and the first and second intermediate arms 21 and 22 are difficult to hit at the edge and corner of the swash plate arm 11b. Thereby, twisting can be further prevented. Other functions and effects are the same as those of the first embodiment.

  In the compressor of Example 21, a thrust plate 67 and a lug member 68 are press-fitted into the drive shaft 6 as shown in FIG. The thrust plate 67 is made of an aluminum-based material for weight reduction and the like. Since the lug member 68 rotates in synchronization with the drive shaft 6 and transmits torque to the swash plate 11 via the link mechanism 71, the lug member 68 is formed of an iron-based material as with the drive shaft 6. The lug side pin 23 is orthogonal to the central axis O of the drive shaft 6.

  A washer 69 made of an anti-vibration alloy is provided between the thrust plate 67 and the lug member 68. One support portion 11g protrudes from the bottom dead center side of the surface of the swash plate 11 on the lug member 68 toward the washer 69, and the support portion 11g contacts the rear surface of the washer 69 when the swash plate 11 is at the maximum inclination angle. It is like that. In the compressor of the twenty-first embodiment, the link mechanism 71 is configured as described above. Other configurations are the same as those of the first embodiment.

  In this compressor, even if the lug member 68 and the thrust plate 67 cause relative rotation, it is possible to effectively prevent wear of both. In addition, since the support portion 11g of the swash plate 11 abuts against the washer 69, it is possible to prevent wear of both the thrust plate 67 and the swash plate 11 even if relative rotation occurs. Furthermore, since the washer 69 is made of a vibration-proof alloy, noise and vibration can be reduced.

  In the compressor of Example 22, as shown in FIG. 31, an insertion hole 72a is provided through the thrust plate 72, and the drive shaft 6 is inserted through the insertion hole 72a. Thus, the thrust plate 72 is loosely fitted to the drive shaft 6. A lug member 68 is press-fitted into the drive shaft 6. In the compressor of the twenty-second embodiment, the link mechanism 73 is configured as described above. Other configurations are the same as those in the twenty-first embodiment.

  This compressor can achieve the same effects as those of the twenty-first embodiment.

  As shown in FIGS. 32 and 33, in the compressor of Example 23, an insertion hole 75a is provided through the thrust plate 75, and the drive shaft 74 is inserted through the insertion hole 75a. Thus, the thrust plate 75 is loosely fitted to the drive shaft 74.

  On the drive shaft 74, a bulging portion 74a as a lug member is formed with a large diameter behind a portion where the thrust plate 75 is loosely fitted. Further, a press-fitting hole 74b orthogonal to the central axis O is provided through the bulging portion 74a. A press-fitting hole 11h is provided in the swash plate arm 11b of the swash plate 11 in parallel with the press-fitting hole 74b.

  Insertion holes 21e, 21f, 22e, and 22f are provided at both ends of the first and second intermediate arms 21 and 22, respectively. The press-fitting holes 74 b and 11 h have a press-fitting allowance for the lug-side pin 23 and the swash plate-side pin 24, and the insertion holes 21 e, 21 f, 22 e and 22 f are slightly more than the lug-side pin 23 and the swash plate-side pin 24. It has a large diameter. Thus, in this compressor, the lug-side pin 23 is loosely fitted into the first and second intermediate arms 21 and 22 while being press-fitted into the bulging portion 74a, and the swash plate-side pin 24 is press-fitted into the swash plate arm 11b. 2 are freely fitted to the intermediate arms 21 and 22.

  The thrust plate 75 is formed with side walls 75b and 75c located on both end sides of the lug-side pin 23. The inner surfaces of the side walls 75b and 75c are guide surfaces 75d and 75e for guiding the outer surfaces 21a and 22a of the first and second intermediate arms 21 and 22, respectively. The guide surfaces 75d and 75e of the side walls 75b and 75c prevent the first and second intermediate arms 21 and 22 from coming off from the lug side pin 23 and the swash plate side pin 24. In the compressor of the twenty-third embodiment, the link mechanism 76 is configured as described above. Other configurations are the same as those of the tenth embodiment.

  In this compressor, even if the moment acting on the swash plate 11 is large, the first and second intermediate arms 21 and 22 loosely fitted to the lug-side pin 23 and the swash plate-side pin 24 are protruded from the swash plate arm 11b. Thrust load can be transmitted stably to 74a. Further, since the side walls 75b and 75c of the thrust plate 75 can reinforce the first and second intermediate arms 21 and 22, the thickness of the first and second intermediate arms 21 and 22 can be reduced, the weight of the link mechanism 75 can be reduced, and the rotation balance can be reduced. Can be improved. Other functions and effects are the same as those of the first embodiment.

  In the compressor of Example 24, as shown in FIG. 34, the first and second intermediate arms 77 and 78 in which the thickness around the lug side pin 23 is thicker than the thickness around the swash plate side pin 24 in the rotation direction of the drive shaft 74. Is adopted. In the compressor of the twenty-fourth embodiment, the link mechanism 79 is configured as described above. Other configurations are the same as those in the twenty-third embodiment.

  In this compressor, the first and second intermediate arms 77 and 78 are loosely fitted with the lug side pins 23 in a larger length than the swash plate side pins 24, and the first and second intermediate arms 77 and 78 are swash plate 11. It becomes difficult to incline in the direction of rotation. For this reason, the first and second intermediate arms 77 and 78 are difficult to be removed from the lug-side pin 23 and the swash plate-side pin 24 due to the effects of the side walls 75b and 75c, and the link mechanism 79 is less rugged and stable in operation. . For this reason, noise and abnormal noise are reduced in the compressor. Other functions and effects are the same as those of the twenty-third embodiment.

  In the compressor of Example 25, as shown in FIG. 35, an insertion hole 59a is formed through the thrust plate 59, and the drive shaft 82 is inserted through the insertion hole 59a. Thus, the thrust plate 59 is loosely fitted to the drive shaft 82.

  The drive shaft 82 is formed with a bulging portion 82a as a lug member with a large diameter behind the portion where the thrust plate 59 is loosely fitted. Further, a bearing hole 82b is provided through the bulging portion 82a. The swash plate arm 11b of the swash plate 11 is provided with a bearing hole 82c extending in parallel with the bearing hole 82b.

  Plain bearings 83 and 84 are press-fitted into the bearing holes 82b and 82c, and the lug side pins 23 and the swash plate side pins 24 are housed in the plain bearings 83 and 84 so as to be slidable. The lug side pin 23 and the swash plate side pin 24 are press-fitted into the first and second intermediate arms 21 and 22. In the compressor of the twenty-fifth embodiment, the link mechanism 85 is configured as described above. Other configurations are the same as those of the tenth embodiment.

  In this compressor, the slidability between the bulging portion 82a and the lug side pin 23 and between the swash plate arm 11b and the swash plate side pin 24 is improved, and the operability and quietness of the link mechanism 85 are improved. . Other functions and effects are the same as those of the first embodiment. In place of the plain bearings 83 and 84, a bearing using a roller or a ball may be employed.

  In the compressor of the twenty-sixth embodiment, the thrust plate 59 is loosely fitted to the drive shaft 86 as shown in FIG. On the drive shaft 86, a bulging portion 86a as a lug member is formed with a large diameter behind a portion where the thrust plate 59 is loosely fitted. A press-fitting hole 86b is provided in the bulging portion 86a. The swash plate arm 11b of the swash plate 11 has a press-fitting hole 11h extending in parallel with the press-fitting hole 86b.

  The first and second intermediate arms 87 and 88 have bearing holes 87a, 87b, 88a and 88b penetrating at both ends. Plain bearings 89, 91, 92, 93 are press-fitted into the bearing holes 87 a, 87 b, 88 a, 88 b, and the lug-side pin 23 and the swash plate-side pin 24 are rotated and slid into the plain bearings 89, 91, 92, 93. It is stored movably. The lug side pin 23 and the swash plate side pin 24 are press-fitted into the bulging portion 86a and the swash plate arm 11b. In the compressor of the twenty-sixth embodiment, the link mechanism 94 is configured as described above. Other configurations are the same as those of the tenth embodiment.

  This compressor can achieve the same effects as those of the twenty-fifth embodiment. In place of the plain bearings 89, 91, 92, 93, a bearing using a roller or a ball can be employed.

  In the above, the present invention has been described with reference to Examples 1 to 26. However, the present invention is not limited to the above Examples 1 to 26, and can be appropriately modified and applied without departing from the spirit thereof. Needless to say.

  For example, the lug-side axis and the swash plate-side axis may be supported by bolts.

In addition, when the lag side axis cannot be positioned at the bottom dead center side, such as when the refrigerant is CO ₂ , the lag side axis may intersect the central axis O of the drive shaft, It may be at the top dead center.

  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 perspective view of a link mechanism according to a compressor of Example 1. FIG. 1 is a schematic longitudinal sectional view of a link mechanism according to a compressor of Example 1. FIG. 1 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 1. FIG. It is a schematic longitudinal cross-sectional view of a link mechanism in connection with the compressor of Example 2. FIG. 6 is a schematic cross-sectional view of a link mechanism according to the compressor of Embodiment 2. It is a schematic longitudinal cross-sectional view of a link mechanism in connection with the compressor of Example 3. FIG. 6 is a schematic side view of a link mechanism according to a compressor of Example 4. FIG. 10 is a schematic side view of a link mechanism according to a compressor of Example 5. FIG. 10 is a schematic side view of a link mechanism according to a compressor of Example 6. FIG. 10 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 7. FIG. 10 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 8. FIG. 10 is a schematic side view of a link mechanism according to a compressor of Example 9. FIG. 14 is a schematic side view of a link mechanism according to the compressor of Example 10. FIG. 15 is a schematic side view of a link mechanism according to the compressor of Example 11. FIG. 15 is a schematic side view of a link mechanism according to a compressor of Example 12. FIG. 15 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 12. FIG. 15 is a schematic side view of a link mechanism according to a compressor of Example 13. FIG. 15 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 13. FIG. 16 is a schematic side view of a link mechanism according to a compressor of Example 14. FIG. 16 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 14. FIG. 16 is a schematic side view of a link mechanism according to a compressor of Example 15. FIG. 16 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 15. FIG. 16 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 16. FIG. 15 is a schematic side view of a link mechanism according to a compressor of Example 17. FIG. 15 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 17; FIG. 19 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 18. FIG. 30 is a schematic axial cross-sectional view of a link mechanism according to a compressor of Example 19. FIG. 20 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 20; FIG. 26 is a schematic side view of a link mechanism according to the compressor of Example 21. FIG. 25 is a schematic side view of a link mechanism according to a compressor of Example 22. FIG. 25 is a schematic side view of a link mechanism according to a compressor of Example 23. FIG. 25 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 23. FIG. 25 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 24. FIG. 25 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 25. FIG. 26 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 26. It is a schematic cross-sectional view of a link mechanism according to a conventional compressor.

Explanation of symbols

1b ... Cylinder bore 1, 2, 4 ... Housing (1 ... Cylinder block, 2 ... Front housing, 4 ... Rear housing)
6, 31, 41, 61, 74, 82, 86 ... Drive shaft 10, 33, 41a, 34, 42, 45, 47, 54, 61a, 81, 65, 68, 74a, 82a, 86a ... Lug member (61a 74a, 82a, 86a ... bulge part)
11 ... Swash plate 12, 30, 40, 50, 60, 70, 80, 43, 46, 52, 55, 58, 62, 64, 66, 71, 73, 76, 79, 85, 94 ... Link mechanism 13 ... Pistons 11a, 13a, 14 ... motion conversion mechanism (11a ... shoe sliding surface, 13a ... shoe receiving surface, 14 ... shoe)
11b ... Swash plate arm O ... Center axis P ... Virtual plane A1 ... Lug side axis A2 ... Swash plate side axis 20 ... Intermediate arm 21, 25, 51a, 57, 77, 87 ... First intermediate arm (51a ... Arm part, 57 ... arm)
22, 26, 56a, 78, 88 ... second intermediate arm (56a ... arm portion)
23, 51b, 56b, 61b, 61c ... lug side pin (51b, 56b, 61b, 61c ... pin part)
24, 56c ... swash plate side pin (56c ... pin part)
9, 32, 38, 44, 48, 53, 59, 63, 67, 72, 75 ... Thrust plate 5d ... Thrust bearing 8, 49 ... Lug plate 9b, 34a ... Support part 35a, 36a, 75d, 75e ... Guide surface 35, 36, 75b, 75c ... side wall 22e ... weight part 37, 39 ... spring (37 ... leaf spring, 39 ... torsion coil spring)
42c, 11f, 45c ... relief part 69 ... washer 83, 84, 89, 91, 92, 93 ... bearing (plain bearing)

Claims (25)

A housing having a cylinder bore; a drive shaft rotatably supported by the housing; a lug member that rotates in synchronization with the drive shaft in the housing; and a slant that is supported by the drive shaft in the housing so as to be capable of varying the inclination angle. A plate is provided between the lug member and the swash plate in the housing, and the swash plate cannot be rotated relative to the drive shaft while allowing the tilt angle variation of the swash plate to the drive shaft. A link mechanism, a piston housed in the cylinder bore so as to be able to reciprocate, and a motion that is provided between the swash plate and the piston and that converts the swinging motion of the swash plate into a reciprocating motion of the piston. A conversion mechanism,
The link mechanism includes a swash plate arm protruding from the swash plate toward the lug member, a lug orthogonal to a virtual plane determined by a center axis of the drive shaft and a top dead center position of the swash plate. An intermediate arm pivotally supported by the lug member around a side axis and pivotally supported by the swash plate arm around a swash plate side axis parallel to the lug side axis;
The intermediate arm has a first intermediate arm 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, A variable capacity swash plate compressor, wherein the lug member and the swash plate arm are slidably clamped by the lug side pin and the swash plate side pin.   The lug side pin is press-fitted into the first intermediate arm and the second intermediate arm while being loosely fitted to the lug member, and the swash plate side pin is loosely fitted to the swash plate arm and the first intermediate arm and the The variable displacement swash plate compressor according to claim 1, wherein the compressor is press-fitted into the second intermediate arm.   3. The variable displacement swash plate compressor according to claim 1, wherein the swash plate side axis is located on a top dead center side of the swash plate, and the lug side axis is closer to the drive shaft than the swash plate side axis.   4. The variable displacement swash plate compressor according to claim 3, wherein the lug side axis is located at a bottom dead center side of the swash plate.   A thrust plate that rotates synchronously with the drive shaft and a thrust bearing provided between the thrust plate and the housing are provided in the housing, and the thrust plate and the lug member are integrated with each other. The capacity-variable swash plate compressor according to claim 3 or 4, wherein the compressor is configured.   The lug plate is provided with a support portion that supports at least one anti-swash plate side of the first intermediate arm and the second intermediate arm when the swash plate is at a maximum inclination angle. 6. The variable capacity swash plate compressor according to claim 5, which is located on the dead center side.   A thrust plate that rotates synchronously with the drive shaft and a thrust bearing provided between the thrust plate and the housing are provided in the housing, and the thrust plate is in contact with the lug member or the intermediate arm. The capacity-variable swash plate compressor according to claim 3 or 4, which is in contact therewith.   8. The variable displacement swash plate compressor according to claim 7, wherein the thrust plate is fitted into the drive shaft with a clearance.   9. The variable displacement swash plate compressor according to claim 7, wherein the thrust plate is made of a vibration-proof alloy.   The lug member is provided with a support portion that supports at least one anti-swash plate side of the first intermediate arm and the second intermediate arm when the swash plate is inclined at a maximum angle. The variable displacement swash plate compressor according to any one of claims 7 to 9, which is located on a dead center side.   9. The variable displacement swash plate compressor according to claim 8, wherein the thrust plate is formed with a side wall having a guide surface for guiding an outer surface of the first intermediate arm and an outer surface of the second intermediate arm.   The variable displacement swash plate compressor according to claim 1, wherein the intermediate arm has a weight portion on a bottom dead center side of the swash plate.   A biasing force is applied between the lug member and the intermediate arm, between the thrust plate and the intermediate arm, or between the intermediate arm and the swash plate arm so as to reduce the inclination angle of the swash plate. The capacity-variable swash plate compressor according to claim 5 or 7, wherein a spring having a force is provided.   The variable displacement swash plate compressor according to claim 1, wherein at least one of the lug member and the swash plate arm is formed with an escape portion for avoiding twisting by the first intermediate arm and the second intermediate arm.   The variable displacement swash plate compressor according to claim 2, wherein a gap between the lug member and the lug-side pin is smaller than a gap between the first intermediate arm and the second intermediate arm and the lug member.   The variable displacement swash plate compressor according to claim 2, wherein a gap between the swash plate arm and the swash plate side pin is smaller than a gap between the first intermediate arm and the second intermediate arm and the swash plate arm.   The one of the lug side pin and the swash plate side pin and the first intermediate arm are integrated, and the other of the lug side pin and the swash plate side pin and the second intermediate arm are integrated. Item 2. The variable capacity swash plate compressor according to Item 1.   2. The variable displacement swash plate compressor according to claim 1, wherein the lug side pin and the swash plate side pin are integrated with one of the first intermediate arm and the second intermediate arm.   The variable displacement swash plate compressor according to claim 1, wherein at least one of the drive shaft, the lug member, the lug side pin, the swash plate, the swash plate arm, and the swash plate side pin is integrated.   The variable displacement swash plate compressor according to claim 7, wherein a washer is provided between the lug member and the thrust plate. The lug-side pin is loosely fitted to the first intermediate arm and the second intermediate arm while being press-fitted into the lug member, and the swash plate-side pin is press-fitted into the swash plate arm and the first intermediate arm and the second 2 loosely fitted to the intermediate arm,
2. The variable displacement swash plate compressor according to claim 1, wherein the first intermediate arm and the second intermediate arm are secured from the lug side pin and the swash plate side pin. In the housing, a thrust plate that rotates synchronously with the drive shaft, and a thrust bearing provided between the thrust plate and the housing are provided,
23. The capacity variable type slant according to claim 21, wherein at least one of the thrust plate and the swash plate is formed with a side wall having a guide surface for guiding the outer surface of the first intermediate arm and the outer surface of the second intermediate arm. Plate type compressor.   The first intermediate arm and the second intermediate arm have a thickness around one of the lug side pin and the swash plate side pin larger than the thickness around the other in the rotation direction of the drive shaft. Variable capacity swash plate compressor.   The variable displacement swash plate compressor according to claim 2, wherein a bearing is provided between at least one of the lug member and the lug side pin and between the swash plate arm 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 the piston, and the shoe sliding surface and the shoe receiving surface. Consisting of a hemispherical shoe,
The variable displacement swash plate compressor according to any one of claims 1 to 24, wherein the swash plate arm is formed so as to avoid being vertically above the shoe sliding surface.

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