JP2009068358A - Variable displacement type swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement type swash plate compressor hard to cause abrasion in a link mechanism and capable of exerting excellent durability. <P>SOLUTION: In the compressor, the link mechanism 10 is formed of a lug plate 8, a swash plate arm 9b and first and second intermediate arms 21, 22. The first and second intermediate arms 21, 22 include pairs of first guided surfaces 21a, 21b, 22a, 22b extending in parallel to a virtual plane P, and having back sides thereof facing each other in front and back in a rotation direction R of a drive shaft 6, and each are formed into a plate shape extending from a lug plate 8 side to a swash plate 9 side. First and second lug arms 8a, 8b of the lug plate 8 are formed with first and second lug side storage recesses 8c, 8f having first guide surfaces 8d, 8e, 8g, 8h. The first and second intermediate arms 21, 22 are stored in the first and second lug-side storage recesses 8c, 8f. <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. 12, the link mechanism is integrated with the lug plate 91, the lug plate 91, and the first and second lug arms 91a, 91b projecting toward the swash plate 92, and the swash plate 92, A swash plate arm 92a protruding toward the lug plate 91, a first intermediate arm 93 provided between the first lug arm 91a and the swash plate arm 92a, and a second lug arm 91b and the swash plate arm 92a. And a second intermediate arm 94 provided therebetween.

  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 compressor 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 rotates in the rotational direction R, each piston reciprocates in the cylinder bore via the swing plate and each piston rod. The refrigerant gas is sucked into the compression chamber, and the refrigerant gas is 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 respectively in the front and rear in the rotational direction R of the drive shaft. The guided 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. It guides with the other side of 92a. Since the inner surface of the first lug arm 91a and one side surface of the swash plate arm 92a, and the inner surface of the second lug arm 91b and the other side surface of the swash plate arm 92a, the lug plate 91 and the swash plate 92 are separate members. The positions of the first and second intermediate arms 93 and 94, and hence the swash plate 92 are easily distorted and twisted from the normal positions. 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 it is an object to be solved to provide a variable displacement swash plate compressor that is less likely to cause wear in the link mechanism and can exhibit excellent durability. It is said.

  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 fixed to the drive shaft within 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 lug member. 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 is integrated with the lug member and the swash plate, and is provided between the lug member arm protruding from the lug member side, the lug member and the swash plate arm, and the center of the drive shaft. The swash plate is supported by the lug member around the lug side axis perpendicular to the virtual plane determined by the axis and the top dead center position of the swash plate, and around the swash plate side axis parallel to the lug side axis. In a variable displacement swash plate compressor consisting of an intermediate arm pivotally supported by the arm,

  The intermediate arm is present on one side of the imaginary plane and extends from the lug member side to the swash plate side, and is present on the other side of the imaginary plane from the lug member side. A plate-like second intermediate arm extending to the swash plate side,

  The first intermediate arm has a first guided surface that extends in parallel with the virtual plane and that is paired with the first guided surface in the front and rear in the rotational direction of the drive shaft,

  The second intermediate arm has a second guided surface that extends in parallel with the virtual plane and that forms a pair and is back to the back and forth in the rotational direction of the drive shaft,

  At least one of the lug member and the swash plate arm is formed with a first storage recess that exists on one side of the virtual plane and a second storage recess that exists on the other side of the virtual plane,

  The first storage recess has a first guide surface extending in parallel with the imaginary plane and facing each other in a pair, in front of and behind in the rotational direction of the drive shaft,

  The second storage recess has a second guide surface extending in parallel with the virtual plane and facing each other in a pair, before and after the rotation direction of the drive shaft,

  The first intermediate arm is stored in the first storage recess so that the first guided surfaces are guided by the first guide surfaces, and the second intermediate arm is mounted on the second guide surfaces. Both the second guided surfaces are housed in the second housing recess so as to be guided.

  In the compressor of the present invention, first and second storage recesses are formed in at least one of the lug member and the swash plate arm. Then, both first guided surfaces of the first intermediate arm are guided by both first guide surfaces of the first storage recess, and both second guided surfaces of the second intermediate arm are guided by both second guide surfaces of the second storage recess. It is guided by. Since both the first guide surfaces of the first storage recess and the second guide surfaces of the second storage recess are formed on the same member, their positions do not change. For this reason, the first and second intermediate arms, and hence the swash plate, are easily maintained at regular positions and are not easily twisted.

  Moreover, in the compressor of this invention, since it is not necessary to project a lug member largely to the swash plate side, manufacture of a lug member and by extension, manufacture of the whole compressor becomes easy.

  Therefore, the variable capacity swash plate compressor of the present invention is less likely to wear the link mechanism and can exhibit excellent durability.

  JP-A-2003-172333 discloses another link mechanism as shown in FIG. This link mechanism is integrated with the lug plate 81 and the lug plate 81, and is integrated with the first and second lug arms 81a and 81b protruding toward the swash plate 82 and the swash plate 82, and protrudes toward the lug plate 81. It has one swash plate arm 82a and a U-shaped intermediate arm 83.

  The intermediate arm 83 is pivotally supported on the first and second lug arms 81a and 81b by a lug side pin 84, and is pivotally supported on the swash plate arm 82a by a swash plate side pin 85. The lug-side pin 84 extends in the direction of the lug-side axis A1 orthogonal to the virtual plane P. The swash plate side pin 85 extends in the direction of the swash plate side axis A2 parallel to the lug side axis A1. When the lug plate 81 and the intermediate arm 83 are made of an aluminum-based material, an iron washer is provided between the first and second lug arms 81 a and 81 b and the intermediate arm 83.

  In this link mechanism, the intermediate arm 83 has guided surfaces 83a, 83b on the lug plate 81 side and guided surfaces 83c, 83d on the swash plate 82 side before and after the rotational direction R of the drive shaft. In the intermediate arm 83, guided surfaces 83a and 83b are guided by both inner surfaces of the first and second lug arms 81a and 81b, and guided surfaces 83c and 83d are guided by both side surfaces of the swash plate arm 82a. For this reason, in this link mechanism, it is considered that the intermediate arm 83 and thus the swash plate 82 are not easily twisted.

  However, in this link mechanism, the intermediate arm 83 has a complicated shape, and the intermediate arm 83 is slidably housed between the inner surfaces of the first and second lug arms 81a and 81b. Since both sides of 82a must be slidably housed, the tolerance management is troublesome. Further, when the washers are provided between the first and second lug arms 81a and 81b and the intermediate arm 83, it is troublesome to insert the washers. For this reason, in this compressor, in order to exhibit the outstanding durability, the raise of manufacturing cost will arise.

  On the other hand, in the compressor of the present invention, the first and second intermediate arms of the link mechanism are plate-like, and tolerance management can be simplified as compared with the link mechanism described in the above publication. Moreover, it is not necessary to provide an iron washer between the lug member and the first and second intermediate arms by using an aluminum-based material for the lug plate and an iron-based material for the intermediate arm. For this reason, this compressor can exhibit the outstanding durability, and can also prevent the increase in manufacturing cost.

  In the compressor of the present invention, it is preferable that the first storage recess and the second storage recess are formed in the lug member, and the swash plate arm is in contact with the first intermediate arm and the second intermediate arm on both side surfaces. In this case, the manufacture of the swash plate arm and hence the swash plate can be facilitated, the weight of the swash plate can be reduced, the inertial force of the swash plate can be reduced, and the capacity change response can be accelerated.

  In the compressor according to the present invention, the first storage recess and the second storage recess are formed in the swash plate arm, the lug member has a lug arm protruding to the swash plate side, and the lug arm has the first intermediate arm and the second on both side surfaces. It is also preferable to contact the intermediate arm. In this case, manufacture of a lug arm and by extension, a lug member becomes easy. Moreover, the lug member can be reduced in weight and the inertial force of the lug member can be reduced.

  In the compressor according to the present invention, the first storage recess and the second storage recess may be formed on the lug member and the swash plate arm. In this case, both first guided surfaces of the first intermediate arm are guided by both first guide surfaces of the first storage recess of the lug member and both first guide surfaces of the first storage recess of the swash plate arm. Since the second guided surfaces of the intermediate arm are guided by the second guide surfaces of the second storage recess of the lug member and the second guide surfaces of the second storage recess of the swash plate arm, The intermediate arm, and hence the swash plate, is easier to maintain in a regular position and is less susceptible to twisting.

  It is preferable that the first intermediate arm and the second intermediate arm are pivotally supported on the lug member by a lug side pin having the lug side axis as a central axis. In this case, the first and second intermediate arms are not separated from the lug member, and it is difficult to generate abnormal noise.

  Further, it is preferable that the first intermediate arm and the second intermediate arm are pivotally supported on the swash plate arm by a swash plate side pin having a swash plate side axis as a central axis. In this case, the first and second intermediate arms are not separated from the swash plate arm, and it is difficult to generate abnormal noise.

  The lug member includes a first lug arm that protrudes toward the swash plate and has a first storage recess, and a second lug arm that protrudes toward the swash plate and has a second storage recess. The first lug arm and the second lug arm Meat stealing is preferably formed between the lug arms. In this case, it is possible to reduce the inertia force of the lug member by reducing the weight of the lug member by stealing the meat. It is also possible to use meat theft for assembly.

  If the lug member is reduced in weight, the rotational moment of inertia of the compressor can be reduced with respect to a high-power diesel engine, and a clutch-less operation can be performed against excessive rotational fluctuation transmitted from the engine to the pulley via the belt. If it is a compressor, the malfunctioning by the excessive stress to a torque limiter can be prevented. Further, if the compressor has a clutch against excessive rotation fluctuation transmitted to the pulley, wear of the fastening portion between the drive shaft such as a spline and the hub can be prevented.

  The first intermediate arm is pivotally supported on the first lug arm by a first lug side pin having a lug side axis as a central axis, and the second intermediate arm is second by a second lug side pin having a lug side axis as a central axis. It is preferable that the lug arm is pivotally supported. In this case, the first and second intermediate arms are not separated from the first and second lug arms, and it is difficult to generate abnormal noise. Further, since the total length of the first lug-side pin and the second lug-side pin can be shorter than one lug-side pin, the lug-side pin can be reduced in weight and the inertial force can be reduced. In addition, the centering of the first lug side pin and the second lug side pin can be simplified and the assembling workability can be improved rather than the long lug side pin being assembled so as not to be inclined.

  It is preferable that the first lug-side pin is press-fitted into the first lug arm on the virtual plane side from the first storage recess, and the second lug-side pin is press-fitted into the second lug arm on the virtual plane side from the second storage recess. In this case, the first and second storage arms are not deformed, and the first and second intermediate arms can be suitably guided with high productivity. Further, it is not necessary to prevent the first and second lug pins from coming off.

  The lug member includes a first lug arm that protrudes toward the swash plate and includes a first storage recess, and a second lug arm that protrudes toward the swash plate and includes a second storage recess, and includes the first lug arm and the second lug arm. The lug arm preferably overlaps the swash plate arm in the protruding direction. In this case, the first and second intermediate arms can be more reliably prevented from falling down. Moreover, since the first and second intermediate arms can be thinned, it is possible to optimize the rotation balance and reduce vibration.

  The swash plate side pin is preferably press-fitted at the center of the swash plate arm. In this case, the first and second intermediate arms can be suitably guided under high productivity. Further, it is not necessary to prevent the swash plate side pin from coming off.

  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.

  The lug member is preferably made of an aluminum-based material, and the intermediate arm is preferably made of an iron-based material. In this case, the processing of the aluminum-based material is relatively easy. Further, the inertia force of the lug member is reduced. If the intermediate arm is made of an iron-based material, sliding between the lug member and the intermediate arm is suitably maintained.

  Hereinafter, Embodiments 1 to 5 embodying the present invention will be described with reference to the drawings.

  As shown in FIG. 1, the variable capacity swash plate compressor of the first embodiment has a front housing 2 joined to the front end of the cylinder block 1 and a valve unit 3 at the rear end of the cylinder block 1. The rear housing 4 is joined. 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 serving as a lug member is press-fitted into the drive shaft 6 through a thrust bearing 5 d between the crank housing 7 and the front housing 2. The lug plate 8 is made of an aluminum material (for example, A4000 series T6).

  Further, a swash plate 9 is provided in the crank chamber 7 behind the lug plate 8. Flat shoe sliding surfaces 9 a are formed on the front and rear outer peripheral surfaces on the outer peripheral side of the swash plate 9. The swash plate 9 is obtained by processing a shoe sliding surface 9a and the like on an integral part of an iron-based material (for example, FCD 700). The swash plate 9 is inserted by the drive shaft 6, and the inclination angle is changed by the link mechanism 10 provided between the swash plate 9 and the lug plate 8 in this state.

  The cylinder block 1 is provided with a plurality of cylinder bores 1b extending concentrically extending in the axial direction. A single-headed piston 11 is housed in each cylinder bore 1b so as to be able to reciprocate. A shoe receiving surface 11a, which is recessed in a spherical shape, is provided on the neck portion of each piston 11 so as to face each other. A pair of front and rear shoes 12 are provided between the swash plate 9 and each piston 11. Each shoe 12 has a substantially hemispherical shape. The front / rear shoe sliding surfaces 9a, the front / rear shoe receiving surfaces 11a, and the front / rear shoes 12 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 13 is accommodated in the rear housing 4. The capacity control valve 13 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 13 detects the pressure in the suction chamber 4a, thereby changing the opening 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 15, an expansion valve 16 and an evaporator 17 are connected to the discharge chamber 4 b by a pipe 14, and the evaporator 17 is connected to the suction chamber 4 a by a pipe 14.

  As shown in FIGS. 2 and 3, the link mechanism 10 includes a lug plate 8, first and second lug arms 8 a and 8 b that are integral with the lug plate 8 and project toward the swash plate 9, and the swash plate 9. One swash plate arm 9b which is integrated and protrudes toward the lug plate 8, the first intermediate arm 21 provided between the first lug arm 8a and the swash plate arm 9b, the second lug arm 8b and the swash plate And a second intermediate arm 22 provided between the arm 9b.

  The first and second intermediate arms 21 and 22 are each made of a ferrous material (for example, a hardened product of carbon steel) and have a plate shape extending from the lug plate 8 side to the swash plate 9 side. As shown in FIG. 3, the first intermediate arm 21 extends in parallel with a virtual plane P determined by the central axis of the drive shaft 6 and the top dead center position of the swash plate 9, and forms a pair and faces the back. 1 The guided surfaces 21 a and 21 b are provided in the front and rear in the rotational direction R of the drive shaft 6. The second intermediate arm 22 extends parallel to the virtual plane P, and has second guided surfaces 22 a and 22 b that are paired with each other on the back and forth in the rotational direction R of the drive shaft 6.

  The lug plate 8 is formed with a first lug-side storage recess 8c that exists on one side of the virtual plane P and a second lug-side storage recess 8f that exists on the other side of the virtual plane P. A first lug-side storage recess 8c is formed in the first lug arm 8a. The first lug-side storage recess 8 c extends in parallel with the virtual plane P, and has first guide surfaces 8 d and 8 e that face each other in a pair, in front of and behind the rotation direction R of the drive shaft 6. A second lug-side storage recess 8f is formed in the second lug arm 8b. The second lug-side storage recess 8f extends in parallel with the virtual plane P, and has second guide surfaces 8g and 8h that face each other in a pair, and have a front and rear in the rotational direction R of the drive shaft 6. The distance between the first and second lug-side storage recesses 8 c and 8 f is set larger than the outer diameter of the drive shaft 6. Further, a meat stealer 8i is formed between the first lug arm 8a and the second lug arm 8b.

  The first intermediate arm 21 is stored in the first lug-side storage recess 8c so that the first guided surfaces 21a and 21b are guided by the first guide surfaces 8d and 8e. The second intermediate arm 22 is housed in the second lug-side housing recess 8f so that the second guided surfaces 22a and 22b are guided by the second guide surfaces 8g and 8h.

  A pin hole 8j having a lug side axis A1 orthogonal to the virtual plane P as a central axis extends through the first lug arm 8a, and a lug side axis A2 orthogonal to the virtual plane P is set as a central axis on the second lug arm 8b. A pin hole 8k is formed therethrough. The first intermediate arm 21 has a pin hole 21c perpendicular to the guided surfaces 21a and 21b, and the second intermediate arm 22 has a pin hole 22c perpendicular to the guided surfaces 22a and 22b. Yes.

  The first lug side pin 23 is shorter than the depth of the pin hole 8j of the first lug arm 8a. The first lug-side pin 23 is press-fitted into the pin hole 8j in the range L1 on the imaginary plane P side from the first lug-side storage recess 8c, and is loosely fitted in the pin hole 8j in the other ranges. The first lug-side pin 23 is loosely fitted in the pin hole 21 c of the first intermediate arm 21.

  Similarly, the second lug side pin 24 is shorter than the depth of the pin hole 8k of the second lug arm 8b. The second lug-side pin 24 is press-fitted into the pin hole 8k in the range L2 on the imaginary plane P side from the second lug-side storage recess 8f, and is loosely fitted in the pin hole 8k in the other ranges. The second lug side pin 24 is loosely fitted in the pin hole 22 c of the second intermediate arm 22.

  Thus, the first intermediate arm 21 is pivotally supported on the first lug arm 8 a by the first lug side pin 23, and the second intermediate arm 22 is pivotally supported on the second lug arm 8 b by the second lug side pin 24.

  The swash plate arm 9b is formed so as to avoid the vertical top of the shoe sliding surface 9a. The swash plate arm 9b is provided with a pin hole 9c having a swash plate side axis A3 parallel to the lug side axes A1 and A2 as a central axis. The first intermediate arm 21 has a pin hole 21d penetrating at right angles to the guided surfaces 21a and 21b, and the second intermediate arm 22 has a pin hole 22d penetrating at right angles to the guided surfaces 22a and 22b. Yes.

  The swash plate side pin 25 is press-fitted into the pin hole 9c of the swash plate arm 9b in the central range L3, and is loosely fitted in the pin hole 9c in the other range. The swash plate side pin 25 is loosely fitted in the pin hole 21 d of the first intermediate arm 21 and the pin hole 22 d of the second intermediate arm 22. The first and second lug-side pins 23 and 24 and the swash plate-side pin 25 are made of an iron-based material (for example, a quenched product of SUJ2).

  Thus, the first and second intermediate arms 21 and 22 are pivotally supported on the swash plate arm 9b by the swash plate side pin 25.

  The outer side of the first lug-side storage recess 8c of the first lug arm 8a has a protruding portion 8l that protrudes toward the swash plate 9 side and the outer diameter side compared to the inner side of the first lug-side storage recess 8c of the first lug arm 8a. is doing. Further, the outer side of the second lug-side storage recess 8f of the second lug arm 8b is a protrusion 8m that protrudes toward the swash plate 9 and the outer diameter side compared to the inner side of the second lug-side storage recess 8f of the second lug arm 8b. have. Thus, these projecting portions 8 l and 8 m overlap the swash plate arm 9 b in the projecting direction within the swing range of the first and second intermediate arms 21 and 22. The protruding portions 8l and 8m have both ends of the swash plate side pin 25 exposed.

  As shown in FIG. 2, the lug plate 8 has a weight 8n at the plane symmetrical position of the first and second lug arms 8a and 8b, and the swash plate 9 has a weight 9d at the plane symmetrical position of the swash plate arm 9b. ing. The front end and the inner surface of the weight 9d are in contact with the lug plate 8 when the swash plate 9 has the maximum displacement with the greatest inclination with respect to the plane perpendicular to the central axis of the drive shaft 6.

  The link mechanism 10 is assembled as follows. First, the lug plate 8, the swash plate 9, the first and second intermediate arms 21 and 22, the first and second lug side pins 23 and 24, and the swash plate side pin 25 are prepared. The drive shaft 6 may be press-fitted into the lug plate 8.

  Then, as shown in FIG. 6A, the first and second intermediate arms 21 and 22 are inserted into the first and second lug side housing recesses 8 c and 8 f of the lug plate 8. At this time, a jig 26 is prepared. The jig 26 includes a main body 26a, an insertion portion 26b that protrudes from the main body 26a and can be inserted into the meat stealer 8i of the lug plate 8, and an elastic material 26c such as a leaf spring provided on both side surfaces of the main body 26a. Then, the insertion portion 26b is inserted into the meat stealer 8i and positioned, and the first and second intermediate arms 21 and 22 are held by the elastic material 26c.

  Next, as shown in FIG. 6B, the first and second intermediate arms 21 and 22 held by the jig 26 are moved so that the pin holes 8j and 8k of the first and second lug arms 8a and 8b and the first The first lug side pin 23 is loosely fitted into the pin holes 8j and 21c from the outside of the first lug arm 8a while aligning the pin holes 21c and 22c of the second intermediate arms 21 and 22.

  If the 1st lug side pin 23 moves to the range L1, as shown in FIG.6 (C), the 1st lug side pin 23 will be press-fit in the pin hole 8j. At this time, excessive press-fitting of the first lug-side pin 23 is suppressed by the insertion portion 26b of the jig 26. For this reason, the lug plate 8 is not used because the outer surface of the first lug arm 8c is positioned, and the processing of the outer surface of the first lug arm 8c can be abolished. In addition, the insertion portion 26b of the jig 26 suppresses deformation of the first lug arm 8a inside the first lug-side storage recess 8c.

  As shown in FIGS. 6D to 6F, the second lug side pin 24 is loosely fitted into the pin holes 8k and 22c from the outside of the second lug arm 8b. In the range L2, the second lug side pin 24 is pinned. Press fit into 8k.

  Next, as shown in FIGS. 7 (G) and 7 (H), the insertion portion 26b moves the jig 26 to the meat stealer 26b while moving the jig 26 forward or backward relative to the paper surface, and the swash plate arm 9b of the swash plate 9 is moved. Insert between the first and second intermediate arms 21 and 22. Then, the jig 26 is removed as shown in FIG.

  Thereafter, as shown in FIG. 7J, a jig 27 is prepared. The jig 27 includes a main body 27a in which a pin storage hole 27b is formed, a positioning pin 27c that can be stored in the pin storage hole 27b, and a spring 27d that has a biasing force in a direction in which the positioning pin 27c protrudes from the pin storage hole 27b. Consists of. Then, the positioning pin 27c is inserted into the pin holes 22d, 9c and 21d while the pin holes 9c of the swash plate arm 9b and the pin holes 21d and 22d of the first and second intermediate arms 21 and 22 are aligned. Then, the swash plate side pin 25 is loosely fitted into the pin holes 21d and 9c from the direction opposite to the jig 27 with respect to the swash plate arm 9b, and the positioning pin 27c is pressed and contracted.

  When the swash plate side pin 25 moves to the range L3, as shown in FIG. 7K, the swash plate side pin 25 is press-fitted into the pin hole 9c, and when the swash plate side pin 25 exceeds the range L3, the swash plate The side pin 25 is loosely fitted into the pin hole 21d. In this way, the link mechanism 10 of Example 1 is obtained. The compressor is assembled by the link mechanism 10.

  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 11 reciprocates in the cylinder bore 1b via the shoe 12. To do. As a result, the volume of the compression chamber formed on the head side of the piston 11 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 by the refrigeration circuit including the compressor, the condenser 15, the expansion valve 16, and the evaporator 17. During this time, the motion conversion mechanism converts the swing motion of the swash plate 9 into the reciprocating motion of the piston 11. Further, the link mechanism 10 prevents the swash plate 9 from rotating relative to the drive shaft 6 while allowing the swash plate 9 to change the tilt angle of the lag plate 8.

  At this time, in this compressor, the first and second lug arms 8a and 8b are formed on the lug plate 8, and the first and second lug-side storage recesses 8c and 8f are formed on the first and second lug arms 8a and 8b. Then, both first guided surfaces 21a, 21b of the first intermediate arm 21 are guided by both first guide surfaces 8d, 8e of the first lug-side storage recess 8c, and both second guided surfaces of the second intermediate arm 22 are guided. 22a and 22b are guided by both second guide surfaces 8g and 8h of the second lug-side storage recess 8f. Both the first guide surfaces 8d and 8e of the first lug-side storage recess 8c and the second guide surfaces 8g and 8h of the second lug-side storage recess 8f are formed on the same lug plate 8, so that The position does not change. For this reason, the 1st, 2nd intermediate arms 21 and 22 and by extension, the swash plate 9 are easily maintained at the normal positions.

  In the link mechanism 10 of this compressor, the reaction force of each part when the thrust load F1 acts on the swash plate 9 is shown in FIG. FIG. 4 shows a case where the gap between the first and second lug-side storage recesses 8c and 8f and the first and second intermediate arms 21 and 22 is relatively large. As can be seen from FIG. 4, in this link mechanism 10, each part can suitably disperse the thrust load F <b> 1.

  Further, in the link mechanism 10 of this compressor, the reaction force of each part when the radial load F2 is applied to the swash plate 9 is shown in FIG. FIG. 5 also shows a case where the gap between the first and second lug-side storage recesses 8c and 8f and the first and second intermediate arms 21 and 22 is relatively large. From FIG. 5, it can be seen that in this link mechanism 10, each part can also disperse the radial load F2 appropriately.

  For this reason, when the thrust load F1 and the radial load F2 are applied to the swash plate 9, the link mechanism 10 can be configured such that the reaction force of each part is a thrust force and a relatively small radial force, and is difficult to twist. Recognize.

  Further, in this compressor, it is not necessary to make the first and second lug arms 8a and 8b protrude greatly toward the swash plate 9 side. For this reason, the lug plate 8 is easily cast or forged. Since the distance between the first and second lug-side storage recesses 8c and 8f is larger than the outer diameter of the drive shaft 6, the first and second lug-side storage recesses after the lug plate 8 is press-fitted into the drive shaft 6. Slotting of 8c and 8f can be performed. For this reason, the influence of the deformation | transformation by the press injection of the drive shaft 6 is not given to the 1st, 2 lug side accommodation recessed parts 8c and 8f. Further, since the lug plate 8 is made of an aluminum-based material, the lug plate 8 can be easily processed as compared with a lug plate made of cast iron. For this reason, manufacture of the whole compressor is also easy. Further, in this compressor, the first and second intermediate arms 21 and 22 of the link mechanism 10 are plate-shaped, and tolerance management can be simplified as compared with the conventional link mechanism.

  Therefore, the compressor is less likely to wear the link mechanism 10, can exhibit excellent durability, and can prevent an increase in manufacturing cost.

  Further, in this compressor, the first and second lug side storage recesses 8c and 8f are formed in the lug plate 8, and the swash plate arm 9b is in contact with the first and second intermediate arms 21 and 22 on both side surfaces. The manufacture of the swash plate arm 9b, and hence the swash plate 9, is facilitated, and the weight of the swash plate 9 is reduced to reduce the inertial force of the swash plate 9, thereby making it possible to speed up the capacity change response.

  Further, in this compressor, the first and second intermediate arms 21 and 22 are pivotally supported on the lug plate 8 by the first and second lug-side pins 23 and 24. The first and second intermediate arms 21 and 22 are pivotally supported by the swash plate arm 9b by swash plate side pins 25. For this reason, the first and second intermediate arms 21 and 22 are not separated from the lug plate 8 and the swash plate arm 9b, and it is difficult for noise to occur.

  In this compressor, since the meat stealing 8i is formed between the first lug arm 8a and the second lug arm 8b, the lug plate 8 is reduced in weight by the meat stealing 8i and the inertia force of the lug plate 8 is reduced. is doing. In this compressor, the first and second lug-side pins 23 and 24 are shorter than the depths of the pin holes 8j and 8k of the first and second lug arms 8a and 8b. The total length with the lug-side pin 24 is shortened only for the portion of the meat stealing 8i. For this reason, the inertial force is reduced by the weight reduction of the first and second lug-side pins 23 and 24. In particular, in this compressor, since the lug plate 8 is made of an aluminum-based material, the inertia force of the lug plate 8 is reliably reduced. For this reason, it is possible to improve the durability of the torque limiter provided as necessary, and to prevent wear of the fastening portion of the clutch.

  On the other hand, in this compressor, the first and second intermediate arms 21 and 22 are thin plate-shaped, adopt the first and second lug side pins 23 and 24, and adopt the meat stealing 8i. Moreover, the small balance effect of the weight 8n due to the lug plate 8 made of an aluminum-based material can be eliminated, and vibration noise during high-speed rotation can be suppressed.

  Further, in this compressor, since the total length of the first lug side pin 23 and the second lug side pin 24 is shortened only by the portion of the meat stealing 8i, the long lug side pin is assembled so as not to be inclined. However, the centering of the first lug side pin 23 and the second lug side pin 24, that is, the lug side axes A1 and A2 can be easily made coaxial, and the assembly workability is also improved.

  Further, in this compressor, the first lug-side pin 23 is press-fitted in the first lug arm 8a on the virtual plane P side from the first lug-side storage recess 8c, and the second lug-side pin 24 is hypothesized from the second lug-side storage recess 8f. It is press-fitted into the second lug arm 8b on the plane P side. The swash plate side pin 25 is press-fitted at the center of the swash plate arm 9b. Therefore, the first and second lug-side storage recesses 8c and 8f are not deformed, and the first and second intermediate arms 21 and 22 can be suitably guided with high productivity. Further, it is not necessary to prevent the first and second lug side pins 21 and 22 and the swash plate side pin 25 from coming off.

  Further, in this compressor, since the first and second lug arms 8a and 8b are overlapped with the swash plate arm 9b by the protruding portions 8l and 8m, the first and second intermediate arms 21 and 22 are more reliably prevented from falling down. ing. Moreover, since the 1st, 2nd intermediate arms 21 and 22 can be made thin by this, a rotation balance can be optimized and a vibration can also be reduced. Further, the projecting portions 8l and 8m also function as a stopper for removing the swash plate side pin 25.

  Further, in this compressor, there is one swash plate arm 9b, and this swash plate arm 9b is formed so as to avoid being vertically above the shoe sliding surface 9a. The sliding surface 9a 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 FIG. The link mechanism 30 is integrated with the lug plate 28, the lug plate 28, and one lug arm 28a projecting to the swash plate 9 side, and one lug plate 28 projecting to the lug plate 28 side. Swash plate arm 9b, and first and second intermediate arms 21 and 22 provided between the lug arm 28a and the swash plate arm 9b.

  First and second lug side storage recesses 8c and 8f are formed in the lug arm 28a. The lug stealing 8i like the link mechanism 10 of the first embodiment is not formed on the lug arm 28a. The lug arm 28a is provided with a pin hole 28b having a lug side axis A4 orthogonal to the virtual plane P as a central axis. The lug side pin 29 is shorter than the depth of the pin hole 28b of the lug arm 28a. The lug-side pin 29 is press-fitted into the pin hole 28b in the range L4 outside the second lug-side storage recess 8f, and is loosely fitted in the pin hole 28b in the other ranges. The lug-side pin 29 is loosely fitted into the pin holes 21c and 22c of the first and second intermediate arms 21 and 22.

  Thus, the first and second intermediate arms 21 and 22 are pivotally supported on the lug arm 28 a by the lug side pins 29. Other configurations are the same as those of the link mechanism 10 of the first embodiment, and the same configurations are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, although the lug plate 28 and the lug-side pin 29 are slightly heavy, other operational effects can be achieved in the same manner as the compressor of the first embodiment.

  The compressor of Example 3 employs a link mechanism 40 shown in FIG. The link mechanism 40 is integrated with the lug plate 31, the lug plate 31, one lug arm 31 a that protrudes toward the swash plate 32, and the swash plate 32, and the first that protrudes toward the lug plate 31. 2 swash plate arms 32a and 32b, and first and second intermediate arms 21 and 22 provided between the lug arm 31a and the first and second swash plate arms 32a and 32b.

  The swash plate 32 is formed with a first swash plate-side storage recess 32 c that exists on one side of the virtual plane P and a second swash plate-side storage recess 32 f that exists on the other side of the virtual plane P. A first swash plate side receiving recess 32c is formed in the first swash plate arm 32a. The first swash plate-side storage recess 32 c extends in parallel with the virtual plane P, and has first guide surfaces 32 d and 32 e facing each other in a pair in front and rear in the rotational direction R of the drive shaft 6. A second swash plate-side storage recess 32f is formed in the second swash plate arm 32b. The second swash plate-side storage recess 32f extends in parallel with the virtual plane P, and has second guide surfaces 32g and 32h facing each other in a pair in front and rear in the rotational direction R of the drive shaft 6. The distance between the first and second swash plate-side storage recesses 32 c and 32 f is larger than the outer diameter of the drive shaft 6. A meat steal 32i is formed between the first swash plate arm 32a and the second swash plate arm 32b.

  The lug arm 31a is provided with a pin hole 31b having a lug side axis A5 orthogonal to the virtual plane P as a central axis. The lug side pin 33 is press-fitted into the pin hole 31b of the lug arm 31a in the central range L5, and is loosely fitted in the pin hole 31b in the other range. The lug-side pin 33 is loosely fitted into the pin hole 21c of the first intermediate arm 21 and the pin hole 22c of the second intermediate arm 22.

  The first and second swash plate arms 32a and 32b are formed so as to avoid the vertical top of the shoe sliding surface 9a. The first swash plate arm 32a is provided with a pin hole 32j having a swash plate side axis A6 parallel to the lug side axis A5 as a central axis, and the second swash plate arm 32b is parallel to the lug side axis A5. A pin hole 32k having a swash plate side axis A7 as a central axis is provided.

  The first swash plate side pin 34 is press-fitted into the pin hole 32j in the range L6 on the imaginary plane P side from the first swash plate side accommodation recess 32c, and is loosely fitted in the pin hole 32j in the other ranges. Further, the first swash plate side pin 34 is loosely fitted in the pin hole 21 d of the first intermediate arm 21.

  Similarly, the second swash plate side pin 35 is press-fitted into the pin hole 32k in the range L7 on the imaginary plane P side from the second swash plate side housing recess 32f, and loosely fitted in the pin hole 32k in the other ranges. The second swash plate side pin 35 is loosely fitted in the pin hole 22 d of the second intermediate arm 22.

  Thus, the first and second intermediate arms 21 and 22 are pivotally supported on the lug arm 31 a by the lug side pins 33. The first and second intermediate arms 21 and 22 are pivotally supported by first and second swash plate arms 32a and 32b by first and second swash plate pins 34 and 35, respectively. The lug arm 31a protrudes from the first swash plate side receiving recess 32c of the first swash plate arm 32a and outside the second swash plate side receiving recess 32f of the second swash plate arm 32b, as in the first embodiment. It is also possible to provide protrusions that overlap in the direction. Other configurations are the same as those of the link mechanism 10 of the first embodiment, and the same configurations are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, the first and second swash plate-side storage recesses 32c and 32f are formed in the swash plate 32, and the lug arm 31a is in contact with the first and second intermediate arms 21 and 22 on both side surfaces. As a result, manufacture of the lug plate 31 becomes easy. Moreover, the lug plate 31 can be reduced in weight and the inertial force of the lug plate 31 can be reduced. About another effect, it can show similarly to the compressor of Example 1.

  The compressor of the fourth embodiment employs a link mechanism 50 shown in FIG. The link mechanism 50 is integrated with the lug plate 41 and the lug plate 41, and is integrated with the first and second lug arms 41a and 41b protruding toward the swash plate 32 and the swash plate 32, and protrudes toward the lug plate 41. First and second swash plate arms 32a and 32b, and first and second intermediate arms 21 and 22 provided between the first and second lug arms 41a and 41b and the first and second swash plate arms 32a and 32b. Have.

  The lug plate 41 is formed with a first lug-side storage recess 41c that exists on one side of the virtual plane P and a second lug-side storage recess 41f that exists on the other side of the virtual plane P. A first lug-side storage recess 41c is formed in the first lug arm 41a. The first lug-side storage recess 41 c extends in parallel with the virtual plane P, and has first guide surfaces 41 d and 41 e that face each other in a pair in front and rear in the rotational direction R of the drive shaft 6. Further, a second lug-side storage recess 41f is formed in the second lug arm 41b. The second lug-side storage recess 41f extends in parallel with the virtual plane P, and has second guide surfaces 41g and 41h that face each other in a pair, in front of and behind the rotation direction R of the drive shaft 6. The distance between the first and second lug-side storage recesses 41 c and 41 f is set larger than the outer diameter of the drive shaft 6. Further, a meat steal 41i is formed between the first lug arm 41a and the second swash plate arm 41b.

  A pin hole 41j having a lug side axis A8 orthogonal to the imaginary plane P as a central axis extends through the first lug arm 41a, and a lug side axis A9 orthogonal to the imaginary plane P is defined as a central axis on the second lug arm 41b. A pin hole 41k is formed therethrough.

  The first lug-side pin 42 is press-fitted into the pin hole 41j in the range L8 on the imaginary plane P side from the first lug-side storage recess 41c, and is loosely fitted in the pin hole 41j in the other ranges. The first lug side pin 42 is loosely fitted in the pin hole 21 d of the first intermediate arm 21.

  Similarly, the second lug-side pin 43 is press-fitted into the pin hole 41k in the range L9 on the virtual plane P side from the second lug-side storage recess 41f, and is loosely fitted in the pin hole 41k in the other ranges. Further, the second lug side pin 43 is loosely fitted in the pin hole 22 d of the second intermediate arm 22.

  Thus, the first and second intermediate arms 21 and 22 are pivotally supported on the first and second lug arms 41a and 41b by the first and second lug-side pins 42 and 43, respectively. The first and second intermediate arms 21 and 22 are pivotally supported by first and second swash plate arms 32a and 32b by first and second swash plate pins 34 and 35, respectively. Other configurations are the same as those of the link mechanism 10 of the first and third embodiments, and the same configurations are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, the lug plate 8 is formed with first and second lug side storage recesses 41c and 41f, and the swash plate 32 is formed with first and second swash plate side storage recesses 32c and 32f. Therefore, both first guided surfaces 21a, 21b of the first intermediate arm 21 are both first guide surfaces 41d, 41e of the first lug-side storage recess 41c and both first guide surfaces of the first swash plate-side storage recess 32c. The second guided surfaces 22a and 22b of the second intermediate arm 22 are guided by the second guide surfaces 41g and 41h of the second lug side storage recess 41f and the second swash plate side storage recess 32f. Since the second and second guide surfaces 32g and 32h are guided, the first and second intermediate arms 21 and 22 and thus the swash plate 32 are easily maintained at the normal positions and are less likely to be twisted. About another effect, it can show similarly to the compressor of Example 1.

  The compressor of the fifth embodiment employs a link mechanism 60 shown in FIG. In the link mechanism 60, screw holes 51 c and 51 d are formed in the lug plate 51 and the first and second lug arms 51 a and 51 b of the lug plate 51. The screw holes 51c and 51d are formed only outside the first and second lug-side storage recesses 8c and 8f. Bolts 52 and 53 as first and second lug-side pins are screwed into the screw holes 51c and 51d. Pin portions 52 a and 53 b having a length equal to the thickness of the first and second intermediate arms 21 and 22 are formed at the tips of the bolts 52 and 53. A pair of bolts having a pin portion between the head portion and the screw portion may be used, and these may be used instead of the pin 25 provided on the swash plate arm 9c. Other configurations are the same as those of the link mechanism 10 of the first embodiment, and the same configurations are denoted by the same reference numerals and detailed description thereof is omitted.

  Also in this compressor, the same operation effect as the compressor of Example 1 can be produced.

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

  For example, in Examples 1 to 5 described above, a lug plate that is press-fitted into the drive shaft and receives a thrust load with the front housing is employed as the lug member. The lug member may be fixed to the drive shaft while receiving the thrust load. In this case, the lug arm is not formed on the lug member, the swash plate arm is formed on the swash plate, the first and second swash plate side recesses are formed on the swash plate arm, and the lug member is sandwiched between the first and second intermediate arms. However, the first and second intermediate arms may be housed in the first and second swash plate-side housing recesses.

  Further, the support of the lug side axis and the support of the swash plate side axis may be performed by a pin such as a bolt. The lug member and the first and second intermediate arms are not centered on the lug side axis. The first and second intermediate arms and the swash plate arm may swing with respect to each other with the swash plate side axis as the central axis.

  The present invention is applicable to a vehicle air conditioner.

It is sectional drawing of the compressor of Example 1. FIG. 1 is a perspective 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 explanatory drawing of the reaction force which concerns on the compressor of Example 1 and acts on a link mechanism. It is explanatory drawing of the reaction force which concerns on the compressor of Example 1 and acts on a link mechanism. FIGS. (A) to (F) relate to the compressor according to the first embodiment, and are explanatory views showing a method of assembling the link mechanism. FIGS. (G) to (K) are explanatory views showing a method of assembling the link mechanism in the compressor according to the first embodiment. FIG. 6 is a schematic cross-sectional view of a link mechanism according to the compressor of Embodiment 2. FIG. 9 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 3. FIG. 9 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 4. FIG. 10 is a schematic cross-sectional view of a link mechanism according to a compressor of Example 5. It is a typical sectional view of a link mechanism concerning a conventional compressor. FIG. 10 is a schematic cross-sectional view of a link mechanism according to another conventional compressor.

Explanation of symbols

1b ... Cylinder bore 1, 2, 4 ... Housing (1 ... Cylinder block, 2 ... Front housing, 4 ... Rear housing)
6 ... Drive shaft 8, 28, 31, 41, 51 ... Lug member (lug plate)
9, 32 ... Swash plate 10, 30, 40, 50, 60 ... Link mechanism 11 ... Piston 9a, 11a, 12 ... Motion conversion mechanism (9a ... Shoe sliding surface, 11a ... Shoe receiving surface, 12 ... Shoe)
9b, 32a, 32b ... swash plate arm P ... virtual plane A1, A2, A4, A5, A8, A9 ... lug side axis A3, A6, A7 ... swash plate side axis 21, 22 ... intermediate arm (21 ... first intermediate Arm, 22 ... second intermediate arm)
21a, 21b ... 1st guided surface 22a, 22b ... 2nd guided surface 8d, 8e, 32d, 32e, 41d, 41e ... 1st guide surface 8c, 32c, 41c ... 1st accommodation recessed part (8c, 41c ... 1st 1 lug side storage recess, 32c ... 1st swash plate side storage recess)
8g, 8h, 32g, 32h, 41g, 41h ... second guide surface 8f, 32f, 41f ... second storage recess (8f, 41f ... second lug side storage recess, 32f ... second swash plate side storage recess)
8a, 8b, 28a, 31a, 41a, 41b, 51a, 51b ... lug arm (8a, 41a, 51a ... first lug arm, 8b, 41b, 51b ... second lug arm)
23, 24, 29, 33, 42, 43, 52, 53 ... lug side pins (23, 42, 52 ... first lug side pins, 24, 43, 53 ... second lug side pins)
25, 34, 35 ... swash plate side pins (34 ... first swash plate side pins, 35 ... second swash plate side pins)
8i ... Meat stealing 8l, 8m ... Projection

Claims (13)

A housing having a cylinder bore, a drive shaft rotatably supported by the housing, a lug member fixed to the drive shaft in the housing, and a slant supported by the drive shaft in the housing so as to be capable of varying the inclination angle. The 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 lag member to change the inclination angle of the swash plate. 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 is integrated with the lug member and the swash plate, and is provided between the lug member arm protruding from the lug member side, the lug member and the swash plate arm, and the center of the drive shaft. The swash plate is supported by the lug member around the lug side axis perpendicular to the virtual plane determined by the axis and the top dead center position of the swash plate, and around the swash plate side axis parallel to the lug side axis. In a variable displacement swash plate compressor consisting of an intermediate arm pivotally supported by the arm,
The intermediate arm exists on one side of the imaginary plane, extends from the lug member side to the swash plate side, and exists on the other side of the imaginary plane, from the lug member side. A plate-like second intermediate arm extending to the swash plate side,
The first intermediate arm has a first guided surface that extends in parallel with the virtual plane and that is paired with the first guided surface in front and rear in the rotational direction of the drive shaft,
The second intermediate arm has a second guided surface that extends in parallel with the virtual plane and that is paired with the second guided surface in front and rear in the rotational direction of the drive shaft,
At least one of the lug member and the swash plate arm is formed with a first storage recess that exists on one side of the virtual plane and a second storage recess that exists on the other side of the virtual plane,
The first storage recess has a first guide surface that extends in parallel with the virtual plane and faces each other in a pair, and has a front and rear in the rotational direction of the drive shaft,
The second storage recess has a second guide surface extending in parallel with the virtual plane and facing each other in a pair, in front of and behind in the rotational direction of the drive shaft,
The first intermediate arm is stored in the first storage recess so that the first guided surfaces are guided by the first guide surfaces, and the second intermediate arm is mounted on the second guide surfaces. The variable capacity swash plate compressor is housed in the second housing recess so that both of the second guided surfaces are guided.   The variable capacity according to claim 1, wherein the first storage recess and the second storage recess are formed in the lug member, and the swash plate arm is in contact with the first intermediate arm and the second intermediate arm on both side surfaces. Type swash plate compressor.   The first storage recess and the second storage recess are formed in the swash plate arm, and the lug member has a lug arm projecting toward the swash plate, and the lug arm has the first intermediate arm and the second on both side surfaces. 2. The variable displacement swash plate compressor according to claim 1, which is in contact with the intermediate arm.   2. The variable displacement swash plate compressor according to claim 1, wherein the first storage recess and the second storage recess are formed in the lug member and the swash plate arm.   5. The variable displacement swash plate compression according to claim 1, wherein the first intermediate arm and the second intermediate arm are pivotally supported on the lug member by a lug side pin having the lug side axis as a central axis. Machine.   5. The capacity variable type according to claim 1, wherein the first intermediate arm and the second intermediate arm are pivotally supported on the swash plate arm by a swash plate side pin having the swash plate side axis as a central axis. Swash plate compressor.   The lug member includes a first lug arm that protrudes toward the swash plate and includes the first storage recess, and a second lug arm that protrudes toward the swash plate and includes the second storage recess. 3. The variable capacity swash plate compressor according to claim 2, wherein a meat stealer is formed between the first lug arm and the second lug arm.   The first intermediate arm is pivotally supported on the first lug arm by a first lug side pin having the lug side axis as a central axis, and the second intermediate arm is a second lug having the lug side axis as a central axis. The variable displacement swash plate compressor according to claim 7, which is pivotally supported on the second lug arm by a side pin.   The first lug-side pin is press-fitted into the first lug arm on the virtual plane side from the first storage recess, and the second lug-side pin is press-fitted into the second lug arm on the virtual plane side from the second storage recess. The capacity-variable swash plate compressor according to claim 8.   The lug member includes a first lug arm that protrudes toward the swash plate and includes the first storage recess, and a second lug arm that protrudes toward the swash plate and includes the second storage recess. 3. The variable displacement swash plate compressor according to claim 2, wherein the first lug arm and the second lug arm overlap the swash plate arm in the protruding direction.   The variable displacement swash plate compressor according to claim 10, wherein the swash plate side pin is press-fitted at the center of the swash plate arm. 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 11, wherein the swash plate arm is formed so as to avoid being vertically above the shoe sliding surface.   The variable displacement swash plate compressor according to any one of claims 1 to 12, wherein the lug member is made of an aluminum-based material, and the intermediate arm is made of an iron-based material.

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