JP2009236019A - Capacity variable type swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a capacity variable type swash plate compressor capable of adjusting a rotation balance, materializing the suitable actuating property of a link mechanism, and reducing manufacturing cost. <P>SOLUTION: In the compressor, the link mechanisms 12, 30, 40 have one swash plate arm 11b and a middle arm 20. The middle arm 20 has first and second middle arms 21, 22. The first and second middle arms 21, 22 are jornaled to a lug member 10 and an swash plate arm 11b by a lug side pin 23 and a swash plate side pin 24, and fastened so as to slidably clamp the lug member 10 and the swash plate arm 11b by the lug side pin 23 and the swash plate side pin 24. The first and second middle arms 21, 22 are integrated on a lower dead center side of a swash plate 11 to configure a weight portion 27. <P>COPYRIGHT: (C)2010,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. 7, the link mechanism is integrated with the lug plate 91, and is integrated with the first and second lug arms 91a and 91b projecting toward the swash plate 92, and the swash plate 92, and is connected to 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 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 inclination angle variation of the swash plate 92 to be permitted to the lug plate 91.

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.

  Further, in the above compressor, since the weight portion for adjusting the rotation balance of the sub-assembly including the link mechanism and the swash plate 92 is provided on the swash plate 92, the weight of the weight portion is added to the swash plate 92. There is a concern that a large centrifugal force acts on the swinging motion of the swash plate 92 and the tilt angle of the swash plate 92 is difficult to stabilize. In this case, the appropriate operability of the link mechanism is eventually lost. In particular, when the link mechanism as described above is employed, the weight portion must be positioned on the bottom dead center side of the swash plate 92 in order to adjust the rotation balance, which impairs the operability of the link mechanism. It will be.

  Further, when the weight portion is provided on the swash plate 92, the shape of the swash plate 92 becomes complicated. This is the same when the lug plate 91 is provided with a weight portion. In particular, the bottom dead center side of the swash plate 92 and the lug plate 91 has a large space because the piston protrudes greatly from the cylinder bore. In this case, the manufacturing cost increases due to the increase in size and complexity of the compressor.

  The present invention has been made in view of the above-described conventional situation, and is a variable displacement swash plate compressor capable of adjusting the rotation balance, suitable operability of the link mechanism, and reducing the manufacturing cost. Providing is an issue to be solved.

  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 projecting 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 the side pin and pivotally supported by the swash plate arm around the swash plate side pin parallel to the lug side pin;

  The intermediate arm has a first intermediate arm and a second intermediate arm that extend 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 the lug side pin and the swash plate side pin, and the lug member by the lug side pin and the swash plate side pin. And is fastened while slidably holding the swash plate arm,

  The first intermediate arm and the second intermediate arm are integrated on the bottom dead center side of the swash plate to form a weight portion.

  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.

  Further, in this compressor, since the first and second intermediate arms and the weight portion are integrated with each other, the first and second intermediate arms do not move individually, and the first and second intermediate arms, and thus the slanting The board is distorted from its normal position and difficult to twist. 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.

  Further, in this compressor, since the weight portion is provided in the intermediate arm, it is not necessary to provide the weight portion in the swash plate or the lug member. The weight portion of the intermediate arm is positioned on the bottom dead center side of the swash plate, and the rotation balance of the sub-assembly including the link mechanism and the swash plate can be suitably adjusted. For this reason, the inclination angle of the swash plate is stabilized, and suitable operability of the link mechanism can be obtained.

  Further, since the intermediate arm has the weight portion, the structure of the swash plate and the lug member can be simplified, and the compressor is not complicated. In addition, since the link mechanism having the lug side pin and the swash plate side pin has a space on the bottom dead center side, the size of the compressor does not increase by effectively using the space.

  Therefore, the capacity-variable swash plate compressor of the present invention can realize adjustment of rotation balance, suitable operability of the link mechanism, and reduction in manufacturing cost.

  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 bottom dead center side of the swash plate means a half-circular portion of the swash plate including the bottom dead center position of the swash plate, and the top dead center side of the swash plate includes the top dead center position of the swash plate. The half-circle part.

  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, 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. In addition, the thrust plate can be separated from the lug member, and the thrust plate can be loosely fitted to the drive shaft.

  Such a lug member or lug plate may be provided with a support portion for supporting the anti-swash plate side of the intermediate arm when the swash plate has the maximum inclination angle. The compression reaction force transmitted from the piston to the swash plate is received by the support portion of the lug member or the lug plate, and deformation of the link mechanism can be prevented to exhibit excellent durability.

  In the lug member or lug plate, the support portion is preferably 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.

  In the compressor of the present invention, the lug side pin is preferably closer to the drive shaft than the swash plate side pin. In this case, the centrifugal force can be reduced by positioning the weight portion close to the drive shaft, so the load in the direction of increasing the inclination angle of the swash plate is reduced at a high speed, and the inclination angle of the swash plate can be easily controlled. Become. Further, the lubricating oil present in the crank chamber is not agitated unnecessarily, and heating of the lubricating oil is prevented. 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 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 top of the shoe sliding surface. Thus, the swash plate can easily process the shoe sliding surface, and the productivity is improved.

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

  As shown in FIG. 1, the variable capacity swash plate compressor according to the first embodiment includes a cylinder block 1, a front housing 2, and a rear housing 4. A front housing 2 is joined to the front end of the cylinder block 1, and a rear housing 4 is joined to the rear end of the cylinder block 1 via a 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. As shown in FIG. 2, 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.

  As shown in FIG. 3, the lug member 10 is formed in a horseshoe shape having parallel surfaces 10a on the bottom dead center side. Further, an insertion hole 10b orthogonal to both parallel surfaces 10a is formed on the bottom dead center side of the lug member 10. The insertion holes 10b are coaxially arranged on both sides in the width direction of the lug member 10, and are not connected to each other at the center in the width direction of the lug member 10, and are not connected to the press-fit hole 8a. As shown in FIGS. 2 and 3, the insertion hole 10b and the drive shaft 6 are in a positional relationship where they overlap each other in the radial direction, and the insertion of the insertion hole 10b, and hence the lug-side pin 23 described later inserted through the insertion hole 10b, is driven. It is set to be located near the axis 6. Further, the insertion hole 10 b is formed with a slightly larger diameter than the lug side pin 23.

  As shown in FIGS. 1 and 2, the crank chamber 7 is provided with a disk-shaped swash plate 11 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 into the drive shaft 6, and the inclination angle is changed by the link mechanism 12 provided between the swash plate 11 and the lug member 10 in this state. One support portion 11e protrudes from the bottom dead center side of the surface of the swash plate 11 toward the lug member 10 toward the lug member 10, and the tip of the support portion 11e is at the tip of the lag member 10 when the swash plate 11 is at the maximum tilt angle. It comes into contact with the rear surface.

  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 shoes 14 are provided between the swash plate 11 and each piston 13 in the front-rear direction. 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.

  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.

  1-4, the link mechanism 12 is integrated with the swash plate 11, and includes one swash plate arm 11b protruding 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. Further, as shown in FIG. 3, the first and second intermediate arms 21 and 22 have a weight portion 27 on the bottom dead center side of the swash plate 11 and are integrated with each other via the weight portion 27.

  As shown in FIG. 4, the first intermediate arm 21 extends in parallel with a virtual plane P determined by the center axis of the drive shaft 6 and the top dead center position of the swash plate 11, and forms an outer surface that forms a pair and is back from each other. 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 first and second intermediate arms 21 and 22 are bent near the press-fitting holes 21c and 22c, and the upper dead center side arm toward the upper dead center side with the bent portion as a boundary. 28 extends, and a bottom dead center arm 29 extends toward the bottom dead center. Although the extension length of the bottom dead center arm 29 is set to be smaller than the extension length of the top dead center arm 28, the extension end of the bottom dead center arm 29 is the end face 10c ( The surface connected to both parallel surfaces 10a). At the maximum inclination angle of the swash plate 11, the top dead center arm 28 is inclined with respect to the central axis of the drive shaft 6, and the bottom dead center arm 29 is orthogonal to the central axis of the drive shaft 6. Therefore, the bottom dead center arm 29 can avoid interference with the thrust plate 9 and the support portion 11e when the swash plate 11 is at the maximum inclination angle.

  As shown in FIG. 3, the weight portion 27 has a shape that connects the opposing inner surfaces (inner surfaces 21 b and 22 b shown in FIG. 4) of the bottom dead center arm 29 of the first and second intermediate arms 21 and 22. The press-fitting holes 21c, 21d, 22c, and 22d extend in parallel. The extension length of the weight portion 27 is the same as or slightly longer than the distance between the two parallel surfaces 10 a of the lug member 10. Further, the thickness of the weight portion 27 is larger than the thickness of the first and second intermediate arms 21 and 22 excluding itself, and a predetermined weight is given to the weight portion 27. The first and second intermediate arms 21 and 22 are kept at a constant distance by a weight portion 27.

  The bottom dead center side arm 29 and the weight part 27 of the first and second intermediate arms 21 and 22 form a square U shape as a whole, and the bottom dead center side outer surface (both parallel surfaces 10a and end surfaces 10c) of the lug member 10 and The lug member 10 is arranged so as to straddle the bottom dead center side while leaving a slight gap therebetween. Here, as shown in FIG. 1, the weight portion 27 is disposed in a vacant space 7 a surrounded by the thrust plate 9, the lug member 10 and the swash plate 11 in the space on the bottom dead center side of the crank chamber 7. ing.

  As shown in FIGS. 3 and 4, the swash plate arm 11 b is formed to have substantially the same width as between both parallel surfaces 10 a of the lug member 10, and has parallel surfaces 11 c that are back to each other. The swash plate arm 11b is provided with an insertion hole 11d perpendicular to both parallel surfaces 11c. The insertion hole 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, 22c of the first and second intermediate arms 21, 22 are on a virtual plane P determined by the center axis of the drive shaft 6 and the top dead center position of the swash plate 11. It extends in the direction of the orthogonal lug side axis A1. 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 supported by the two lug-side pins 23 while being pivotally supported by the lug member 10 and the swash plate arm 11b by two lug-side pins 23 and one swash plate-side pin 24. And the swash plate side pin 24 and the lug member 10 and the swash plate arm 11b are slidably clamped and fastened. More specifically, each 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 first fitted while being loosely fitted to the swash plate arm 11b. 2 It is press-fitted into the intermediate arms 21 and 22.

  The lug side pin 23 is inserted along the lug side axis A1, and the swash plate side pin 24 is inserted along the swash plate side axis A2. The lug side pin 23 is located on the bottom dead center side, the swash plate side pin 24 is located on the top dead center side, and the lug side pin 23 is closer to the drive shaft 6 than the swash plate side pin 24. Is located. Thus, the lug-side pin 23 is positioned near the drive shaft 6, so that the weight portion 27 can also be positioned near the drive shaft 6. Further, the swash plate arm 11b is formed so as to avoid the vertical top of the shoe sliding surface 11a.

  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 11 rotate synchronously, and the pistons 13 are connected to the cylinder bores 1b via the shoes 14, respectively. Reciprocate. Thereby, each compression chamber formed in the head side of each piston 13 changes volume. For this reason, the refrigerant gas in the suction chamber 4a is sucked into each 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 each 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 this compressor, the first and second intermediate arms 21 and 22 are kept at a constant distance by the weight portion 27, and the lug member 10 and the swash plate arm are formed by the lug side pin 23 and the swash plate side pin 24. 11b is slidably clamped and clamped. 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 the intermediate arm 20 integrated by the weight portion 27, the first and second intermediate arms 21 and 22 do not move individually. The first and second intermediate arms 21 and 22 and the swash plate 11 are not easily distorted from the normal position. Moreover, in this compressor, since it is not necessary to form a lug arm in the lug member 10, manufacture of the lug member 10 and by extension, manufacture of the whole compressor is also easy.

  Further, in this compressor, since the weight portion 27 is provided on the intermediate arm 20, it is not necessary to provide the weight portion on the swash plate 11 or the lug member 10. The weight portion 27 of the intermediate arm 20 is located on the bottom dead center side of the swash plate 11, and the rotation balance of the sub-assembly including the link mechanism 12 and the swash plate 11 can be suitably adjusted. For this reason, the inclination | tilt angle of the swash plate 11 is stabilized, and the suitable operativity of the link mechanism 12 is acquired.

  Further, since the intermediate arm 20 has the weight portion 27, the structure of the swash plate 11 and the lug member 10 can be simplified, and the compressor is not complicated. Further, since the link mechanism 12 having the lug-side pin 23 and the swash plate-side pin 24 has a space 7a on the bottom dead center side, the use of the space 7a does not increase the size of the compressor. .

  Therefore, this capacity variable type swash plate compressor can realize adjustment of the rotation balance, suitable operability of the link mechanism 12, and reduction in manufacturing cost.

  Further, in this compressor, the weight portion 27 is positioned near the drive shaft 6 by positioning the lug side pin 23 closer to the drive shaft 6 than the swash plate side pin 24. Thereby, since the centrifugal force can be reduced, the load in the direction of increasing the tilt angle of the swash plate 11 at a high speed is reduced, and the tilt angle of the swash plate 11 can be easily controlled. Further, the lubricating oil present in the crank chamber 7 is not agitated unnecessarily, and heating of the lubricating oil is prevented. 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.

  The compressor of the second embodiment employs a link mechanism 30 shown in FIG. In the link mechanism 30, the lug member 10 is provided with a support portion 31 that supports the anti-swash plate side of the intermediate arm 20 when the swash plate 11 has the maximum inclination angle. The support portion 31 has a square block shape integrally projecting on the outer surface on the top dead center side of the lug member 10, and is on the surface facing the top dead center side arm 28 of the first and second intermediate arms 21 and 22. The contact surface 31 a extends in a direction inclined with respect to the central axis of the drive shaft 6. Other configurations are the same as those of the first embodiment.

  In this compressor, the compression reaction force transmitted from the piston 13 to the swash plate 11 is received by the support portion 31 of the lug member 10, and deformation of the link mechanism 30 can be prevented to exhibit excellent durability.

  Further, in this compressor, the support portion 31 is disposed at a position substantially symmetrical to the weight portion 27 with the drive shaft 6 interposed therebetween. Thereby, the weight balance between the support part 31 and the weight part 27 becomes more suitable. 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 support portion 32 is provided on the thrust plate 9. The support portion 32 has a plate shape integrally projecting from two locations on the rear surface of the thrust plate 9 toward the swash plate 11, and faces the top dead center side arms 28 of the first and second intermediate arms 21 and 22. The contact surface 32 a extends in a direction inclined with respect to the central axis of the drive shaft 6. Other configurations are the same as those in the first and second embodiments. Also in this compressor, there can exist the same effect as Example 1,2.

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

  For example, if the first and second intermediate arms 21 and 22 can avoid interference with the thrust plate 9, the first and second intermediate arms 21 and 22 may have a shape that extends straight in the entire length direction without having a bent portion. Good.

  Further, if the empty space 7a is ensured, the weight portion 27 is integrated with the first and second intermediate arms 21 and 22 from the end of the first and second intermediate arms 21 and 22, and / or The shape may protrude outward.

  Further, the intermediate arm 20, the lug side pin 23, and the swash plate side pin 24 are press-fitted, the lug member 10 and the lug side pin 23 are loosely fitted, and the swash plate arm 11b and the swash plate side pin 24 are loosely fitted. Instead, the intermediate arm 20 and the lug side pin 23 and the swash plate side pin 24 are loosely fitted, the lug member 10 and the lug side pin 23 are press-fitted, and the swash plate arm 11b and the swash plate side pin 24 are press-fitted. May be.

  Further, the lug side pins 23 do not need to be two, and may be one like the swash plate side pins 24.

  The present invention is applicable to a vehicle air conditioner.

It is a longitudinal cross-sectional view of the compressor of Example 1. 1 is a schematic longitudinal sectional view of a link mechanism according to a compressor of Example 1. FIG. 1 is a schematic side cross-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. FIG. 6 is a schematic side view of a link mechanism according to the compressor of Embodiment 2. FIG. 10 is a schematic side view of a link mechanism according to the compressor of Embodiment 3. 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)
DESCRIPTION OF SYMBOLS 6 ... Drive shaft 10 ... Lug member 11 ... Swash plate 12, 30, 40 ... Link mechanism 13 ... Piston 11a, 13a, 14 ... Motion conversion mechanism (11a ... Shoe sliding surface, 13a ... Shoe receiving surface, 14 ... Shoe)
11b ... Swash plate arm P ... Virtual plane 23 ... Lug side pin 24 ... Swash plate side pin 20 ... Intermediate arm 21 ... First intermediate arm 22 ... Second intermediate arm 27 ... Weight part

Claims (2)

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 projecting 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 the side pin and pivotally supported by the swash plate arm around the swash plate side pin parallel to the lug side pin;
The intermediate arm has a first intermediate arm and a second intermediate arm that extend 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 the lug side pin and the swash plate side pin, and the lug member by the lug side pin and the swash plate side pin. And is fastened while slidably holding the swash plate arm,
The variable displacement swash plate compressor, wherein the first intermediate arm and the second intermediate arm are integrated on the bottom dead center side of the swash plate to form a weight portion.   The variable displacement swash plate compressor according to claim 1, wherein the lug side pin is closer to the drive shaft than the swash plate side pin.

Images