JP2009257204A - Variable displacement swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor capable of materializing suitable operability of a link mechanism and reduction of manufacturing cost, without damaging a function of a channel. <P>SOLUTION: This compressor is provided with the link mechanism 12 including a swash plate arm 11b and first and second intermediate arms 21, 22. The first and second intermediate arms 21, 22 are pivotally supported to a lag member 8 and the swash plate arm 11b by a lag side pin 23 and a swash plate side pin 24, and are fastened by the lag side pin 23 and the swash plate side pin 24 while slidably gripping the lag member 8 and the swash plate arm 11b. The channel 6a extending in an axial direction is formed at a drive shaft 6. The lag side pin 23 includes a small diameter part 23b or a recess space 23c avoiding the channel 6a and is provided near a center axis line A3 of the drive shaft 6. <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. 9, the link mechanism is integrated with the lug plate 91, and is integrated with the first and second lug arms 91a and 91b protruding toward the swash plate 92 and the swash plate 92. 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 tilt angle fluctuation of the swash plate 92 to the drive shaft.

JP-A-10-176658

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

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

  For this reason, the lug plate is abolished, and the lug member and the swash plate arm are supported by the lug side pin and the swash plate side pin while the first and second intermediate arms are pivotally supported by the lug member and the swash plate arm by the lug side pin and the swash plate side pin. A configuration is possible in which the slidable member is slidably clamped. In this case, suitable operability of the link mechanism and reduction in manufacturing cost can be realized.

  However, in a variable displacement swash plate compressor in which a flow path extending in the axial direction is formed on the drive shaft, the lug-side pin closes the flow path of the drive shaft and the refrigerant gas or the like in the flow path is configured in this way. There is a risk of hindering the flow. In this case, the function of the compressor is impaired, such as a change in the discharge capacity of the compressor and a loss of durability.

  The present invention has been made in view of the above-described conventional situation, and can achieve a preferable operability of the link mechanism and a reduction in manufacturing cost, and the function of the flow path is not harmed. Providing a variable capacity swash plate compressor is a problem 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,

A channel extending in the axial direction is formed in the drive shaft,
The lug-side pin is provided in the vicinity of the central axis of the drive shaft while having an escape portion that avoids the flow path.

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

  In this compressor, since the first and second intermediate arms are fastened together by the lug side pin and the swash plate side pin, the first and second intermediate arms do not move individually. 2 The intermediate arm, and hence the swash plate, are not easily distorted from the normal position. 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.

  Furthermore, in this compressor, even if there is a circumstance that the lug side pin is provided in the vicinity of the central axis of the drive shaft, the lug side pin has a relief portion that avoids the flow path of the drive shaft. There is no hindrance to the flow of gas inside.

  Therefore, this compressor can realize suitable operability of the link mechanism and reduction in manufacturing cost, and the function of the flow path is not impaired.

  In addition, if the lug-side pin is provided in the vicinity of the central axis of the drive shaft in this way, the link mechanism can be positioned near the drive shaft, so that the lubricating oil in the crank chamber is prevented from being stirred and heated. As a result, the viscosity of the lubricating oil is difficult to decrease, and high slidability can be secured.

  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.

  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.

  In the compressor of the present invention, the escape portion may be a small diameter portion formed on the lug side pin. According to this, since the first and second intermediate arms can be pivotally supported on the lug member by one lug-side pin, the number of parts can be reduced, and the troublesome part management can be reduced. .

  In the compressor of the present invention, the escape portion may be an escape space formed by dividing the lug side pin. According to this, since the opening degree of a flow path can be enlarged by widening the escape space formed by dividing the lug-side pin, the fluidity of lubricating oil, gas, etc. becomes better.

  Embodiments 1 and 2 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. A plurality of cylinder bores 1 b extending in parallel with the central axis of the drive shaft 6 are provided in the cylinder block 1. Note that the left side in FIG. 1 is the front side, and the right side is the rear side.

  A crank chamber 7 is formed by the front housing 2 and the cylinder block 1, and shaft holes 1 a and 2 a are formed in the front housing 2 and the cylinder block 1. A shaft sealing device 17 and a plain bearing 19 are provided in the shaft hole 2a. A rubber material is used for the shaft seal device 17.

  The rear housing 4 is formed with a suction chamber 4a and a discharge chamber 4b that communicate with each cylinder bore 1b via the valve unit 3. In addition, a storage chamber 54 is formed in the rear housing 4, and a cylindrical cylindrical portion 54 a protrudes downward from the storage chamber 54. The storage chamber 54 and the cylinder portion 54a are oil separators. The discharge chamber 4b and the storage chamber 54 communicate with each other by a discharge passage 4c, and the discharge passage 4c faces the upper portion of the cylindrical portion 54a in the storage chamber 54. The inside of the cylindrical portion 54a is a discharge port 54b. A pipe 56 is connected to the discharge port 54b, and the pipe 56 is connected to the suction chamber 4a via a check valve 57, a condenser 58, an expansion valve 59, and an evaporator 60. A compressor, a check valve 57, a condenser 58, an expansion valve 59, an evaporator 60, and a pipe 56 constitute a refrigeration circuit, and a refrigerant gas mixed with lubricating oil is enclosed in the refrigeration circuit.

  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 4d, and communicates the storage chamber 54 with the crank chamber 7 through the air supply passage 4e. The capacity control valve 15 detects the pressure in the suction chamber 4a, thereby changing the opening of the air supply passage 4e and changing the discharge capacity of the compressor.

  A rear chamber 1c communicating with the shaft hole 1a is formed at the center side of the rear end of the cylinder block 1. The rear chamber 1 c faces the valve unit 3 and communicates with the suction chamber 4 a through a throttle hole 3 a formed on the center side of the valve unit 3. The rear chamber 1c accommodates a cylindrical spacer 62 whose rear end is in contact with the valve unit 3 and whose front end is fitted to the rear end of the drive shaft 6. A diaphragm hole 3 a is disposed opposite to the spacer 62.

  The drive shaft 6 is rotatably supported by a shaft seal device 17 or the like with the front end exposed from the front housing 2 and the center facing the crank chamber 7. As shown in FIGS. 1 and 4, the drive shaft 6 is formed with a flow path 6a extending in the axial direction, and an introduction hole 6b extending in the radial direction is formed perpendicular to the flow path 6a. Yes. The flow path 6a is closed at the front end, opened at the rear end and communicates with the internal space of the spacer 62, and intersects the introduction hole 6b at a position near the front end. The introduction hole 6b is formed between the thrust plate 9 described later and the front housing 2 from the center of the drive shaft 6 to the outer periphery by the radius of the drive shaft 6. In this compressor, the introduction hole 6b, the flow path 6a, the rear chamber 1c, and the throttle hole 3a constitute an extraction passage that connects the crank chamber 7 and the suction chamber 4a.

  The front housing 2 is formed with an oil guide groove 2b extending from the outer peripheral region of the crank chamber 7 to between the front housing 2 and the thrust plate 9 and facing the thrust bearing 5d. The front housing 2 is formed with an oil guide hole 2 c that communicates with the oil guide groove 2 b and faces the plain bearing 19 and the shaft seal device 17. The oil guide hole 2c faces the shaft seal device 17 through the shaft hole 2a and communicates with the introduction hole 6b.

  A lug member 8 is fixed to the drive shaft 6 in the crank chamber 7. 2-5, the lug member 8 is formed with a press-fitting hole 8a, and the drive shaft 6 is press-fitted into the press-fitting hole 8a. As shown in FIG. 5, the lug member 8 is formed in a horseshoe shape having parallel surfaces 8 c back to each other on the bottom dead center side. Further, an insertion hole 8b is formed on the bottom dead center side of the lug member 8 so as to be perpendicular to both parallel surfaces 8c. The insertion hole 8 b is formed with a slightly larger diameter than a later-described large-diameter portion 23 a of the lug-side pin 23 and a slightly smaller diameter than the flow path 6 a of the drive shaft 6. As shown in FIGS. 1 to 5, the insertion hole 8 b extends in the radial direction and penetrates the drive shaft 6, and has a shape communicating with the flow path 6 a at the center in the length direction.

  As shown in FIGS. 1 to 3, a thrust plate 9 is provided between the lug member 8 and the front housing 2. The thrust plate 9 is formed in a disc shape, and a thrust bearing 5 d and a plain bearing 19 are provided between the thrust plate 9 and the front housing 2. In this compressor, the thrust plate 9 is separated from the lug member 8 and is press-fitted into the drive shaft 6. It is also possible to fit the thrust plate 9 to the drive shaft 6 with a clearance.

  Further, a swash plate 11 is provided in the crank chamber 7 behind the lug member 8. As shown in FIG. 2, a flat shoe sliding surface 11 a is 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 so that the inclination angle with respect to the drive shaft 6 can be changed by the link mechanism 12. As shown in FIG. 1, a pressing spring 70 is provided between the lug member 8 and the swash plate 11 to urge the lug member 8 and the swash plate 11 away from each other.

  As shown in FIGS. 2 and 3, the link mechanism 12 is integrated with the swash plate 11, and includes one swash plate arm 11b projecting toward the lug member 8 on the top dead center side, and the lug member 8 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 8 side to the swash plate 11 side, lug side pins 23 and swash plate side pins 24. The first and second intermediate arms 21 and 22 are plate-shaped members extending from the lug member 8 side to the swash plate 11 side.

  As shown in FIG. 3, the first intermediate arm 21 extends in parallel with a virtual plane P determined by the top dead center position and the central axis A3 of the drive shaft 6, and forms an outer surface 21 a and an inner surface that face each other in a pair. 21 b is provided before and after the rotational direction R of the drive shaft 6. The second intermediate arm 22 extends in parallel with the virtual plane P, and has an inner surface 22 a and an outer surface 22 b that are paired with each other and have a 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. At both ends of the second intermediate arm 22, press-fitting holes 22c and 22d is penetrated. The press-fitting holes 21 c and 22 c have a press-fitting allowance for the lug-side pin 23, and the press-fitting holes 21 d and 22 d have a press-fitting allowance for the swash plate side pin 24.

  The swash plate arm 11b is formed to have substantially the same width as between the two parallel surfaces 8c of the lug member 8, and has parallel surfaces 11c that are back to each other. The swash plate arm 11b is provided with an insertion hole 11d extending at right angles to both parallel surfaces 11c. The insertion hole 11 d has a slightly larger diameter than the swash plate side pin 24.

  The insertion hole 8b of the lug member 8 and the press-fit holes 21c and 22c of the first and second intermediate arms 21 and 22 extend in the direction of the lug side axis A1 orthogonal to the virtual plane P. 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 lug side axis A1 and the center axis A3 of the drive shaft 6 are in a positional relationship that intersects each other on the same plane.

  The first and second intermediate arms 21 and 22 are pivotally supported by the lug member 8 and the swash plate arm 11b by the lug side pin 23 and the swash plate side pin 24, and the lug by the lug side pin 23 and the swash plate side pin 24. The member 8 and the swash plate arm 11b are slidably clamped and fastened. Specifically, the lug-side pin 23 is press-fitted into the first and second intermediate arms 21 and 22 while being loosely fitted to the lug member 8, and the swash plate-side pin 24 is loosely fitted to the swash plate arm 11b and first and second intermediates. It is press-fitted into the arms 21 and 22.

  Also, as shown in FIG. 5, large-diameter portions 23a are formed at both ends in the length direction of the lug-side pin 23, and a small-diameter portion having a smaller diameter than the large-diameter portion 23a in the middle of the length direction of the lug-side pin 23. 23b is formed. The small diameter portion 23b is a relief portion. When the small diameter portion 23b is inserted into the insertion hole 8b of the lug member 8, the small diameter portion 23b is disposed in the inner space of the flow path 6a, and forms an escape passage 23d between the inner surface of the flow path 6a. Specifically, the small diameter portion 23b has a narrow body portion 23e in the middle in the length direction, and has tapered portions 23f that gradually increase the diameter dimension toward the large diameter portion 23a at both ends in the length direction. Yes. Among these, only the narrow body part 23e is the part facing the flow path 6a. Further, since the small-diameter portion 23b has the tapered portion 23f, it is possible to avoid stress concentration on the portion connected to the large-diameter portion 23a.

  As shown in FIG. 2, the swash plate arm 11b is formed so as to avoid being vertically above the shoe sliding surface 11a. In addition, one support portion 11e protrudes from the bottom dead center side of the surface of the swash plate 11 on the lug member 8 toward the lug member 8, and the support portion 11e is configured so that the swash plate 11 It comes into contact with the rear surface.

  As shown in FIG. 1, a single-headed piston 13 is accommodated in each cylinder bore 1b so as to reciprocate, and each piston 13 forms a compression chamber in the cylinder bore 1b. A shoe receiving surface 13a, which is recessed in a spherical shape, is provided on the neck portion of each piston 13 so as to face each other. A pair of front and rear shoes 14 is provided between the swash plate 11 and each piston 13. Each shoe 14 has a substantially hemispherical shape. The front and rear shoe sliding surfaces 11a, the front and rear shoe receiving surfaces 13a, and the front and rear shoes 14 constitute a motion conversion mechanism.

  In the compressor configured as described above, when the drive shaft 6 is driven in the rotation direction R, the thrust plate 9, the lug member 8, and the swash plate 11 rotate synchronously, and the piston 13 is connected to the cylinder bore 1b via the shoe 14. Reciprocates inside. Thereby, the volume of the compression chamber formed on the head side of the piston 13 changes. For this reason, the refrigerant gas in the suction chamber 4a is sucked into the compression chamber and compressed, and then discharged into the discharge chamber 4b. In this way, the refrigeration action is performed by the refrigeration circuit. During this time, the motion conversion mechanism converts the swing motion of the swash plate 11 into the reciprocating motion of the piston 13. Further, the link mechanism 12 makes the swash plate 11 relatively unrotatable with respect to the drive shaft 6 while allowing the tilt angle variation of the swash plate 11 to the drive shaft 6.

  Further, as each piston 13 reciprocates, a high-pressure refrigerant gas is discharged into the crank chamber 7 as a blow-by gas from between the cylinder bore 1b and the piston 13. Further, high-pressure lubricating oil and refrigerant gas are supplied from the discharge chamber 4b to the crank chamber 7 through the air supply passage 4e under the control of the capacity control valve 15. If the crank chamber 7 becomes high pressure by the refrigerant gas and the lubricating oil, the back pressure of each piston 13 increases, the inclination angle of the swash plate 11 decreases, and the discharge capacity decreases. Further, the lubricating oil that has entered the crank chamber 7 adheres to and lubricates sliding parts such as between the piston 13 and the cylinder bore 1b and between the swash plate 11 and the shoe 14 in the crank chamber 7.

  On the other hand, the refrigerant gas and the lubricating oil in the crank chamber 7 move to the suction chamber 4a through the introduction hole 6b, the flow path 6a, the rear chamber 1c, and the throttle hole 3a. If the crank chamber 7 has a low pressure, the back pressure of each piston 13 decreases, the inclination angle of the swash plate 11 increases, and the discharge capacity increases. During this time, a large amount of lubricating oil in the crank chamber 7 is present in the outer peripheral region of the front housing 2 by the stirring action of the swash plate 11 and the like, and the lubricating oil is supplied to the thrust bearing 5d through the oil guide groove 2b. The lubricating oil is supplied to the shaft seal device 17 and the plain bearing 19 through the oil guide hole 2c. Thus, the thrust bearing 5d, the shaft seal device 17 and the plain bearing 19 are lubricated.

  The first and second intermediate arms 21 and 22 are fastened while the lug member 8 and the swash plate arm 11b are slidably sandwiched between the lug pin 23 and the swash plate pin 24. The inner surface 21b of the first intermediate arm 21 is guided by the parallel surface 8c of the lug member 8 and the parallel surface 11c of the swash plate arm 11b, and the inner surface 22a of the second intermediate arm 22 is inclined with the parallel surface 8c of the lug member 8. 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. Further, in this compressor, the lug member 8, 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 are selectively assembled. Therefore, the manufacturing cost can be reduced.

  In this compressor, since the first and second intermediate arms 21 and 22 are fastened together by the lug side pin 23 and the swash plate side pin 24, the first and second intermediate arms 21 and 22 are individually provided. It does not move, and the first and second intermediate arms 21 and 22 and thus the swash plate 11 are not easily distorted and twisted from the normal position. Moreover, in this compressor, since it is not necessary to form a lug arm in the lug member 8, manufacture of the lug member 8, and also manufacture of the whole compressor becomes easy.

  Further, in this compressor, the first and second intermediate arms 21 and 22 are pivotally supported on the lug member 8 by the lug-side pin 23 provided in the vicinity of the central axis A3 of the drive shaft 6, so that the link mechanism 12 is The drive shaft 6 is approaching. For this reason, it is difficult to stir the lubricating oil in the crank chamber 7 and the lubricating oil is difficult to be heated. For this reason, the viscosity of lubricating oil is hard to fall and high slidability can be ensured. In particular, the rubber material such as the shaft seal device 17 is hardly deteriorated by the heat of the lubricating oil, and high durability can be exhibited. Further, since the first and second intermediate arms 21 and 22 are pivotally supported in this way, the center of gravity of the link mechanism 12 is close to the center axis A3 of the drive shaft 6 and the centrifugal force is reduced, so that the swash plate 11 can be made at high speed. The load in the direction of increasing the inclination angle of the swash plate 11 is reduced, and the inclination angle of the swash plate 11 can be easily controlled.

  In this compressor, the lug-side pin 23 has a small diameter portion 23b, and a relief passage 23d is formed between the small diameter portion 23b and the inner surface of the flow path 6a. For this reason, the refrigerant gas and the lubricating oil flow to the downstream side of the flow path 6a through the escape path 23d while going around the peripheral surface of the small diameter portion 23b. For this reason, the flow of the refrigerant gas and the lubricating oil is not particularly disturbed by the lug-side pin 23, and good fluidity is ensured.

  Therefore, in this compressor, it is possible to realize a suitable operability of the link mechanism 12 and a reduction in manufacturing cost, and the function of the flow path is not harmed.

  Moreover, in this compressor, since the 1st, 2nd intermediate arms 21 and 22 are pivotally supported by the lug member 8 by one lug side pin 23, the number of parts is reduced and the trouble of parts management is reduced.

  As shown in FIG. 6, the compressor of the second embodiment is different from the first embodiment in the form of the lug-side pin 23 g. Others are the same as those of the first embodiment, and the same reference numerals are given to the same structural parts in the drawings.

  In this compressor, the lug-side pin 23g is divided into two divided pins 23f, and both the divided pins 23f are coaxially inserted from both sides in the width direction with respect to the press-fit holes 21c, 22c and the insertion hole 8b. Yes. The two split pins 23f have the same shape and the same size, and the total length of the both is shorter than the total length of the lug-side pin 23 in the first embodiment. In the state where both split pins 23f are inserted into the press-fit holes 21c, 22c and the insertion hole 8b, the tip in the insertion direction of both split pins 23f faces the flow channel 6a, and between the two tips, An escape space 23c that allows a good flow of refrigerant gas and lubricating oil is formed. For this reason, since the refrigerant gas and the lubricating oil in the flow path 6a pass through the escape space 23c and flow to the downstream side of the flow path 6a, good fluidity is ensured.

  In the second embodiment, the size of the escape space 23c can be easily adjusted by changing the length of the dividing pin 23f. In this case, as shown in FIG. 7, it is also possible to position the tips of both split pins 23f outside the flow path 6a, thereby opening the flow path 6a fully and interfering with the flow of refrigerant gas and lubricating oil. Things are completely eliminated.

  As shown in FIG. 8, the compressor of the third embodiment is different from the first embodiment in the form of the lug-side pin 23 k and the insertion hole 8 e of the lug member 8.

  In this compressor, the lug-side pin 23k is composed of two divided pins 23m as in the second embodiment. Each of the split pins 23m is shorter than the split pin 23m in the second embodiment. Further, the insertion hole 8 e is configured as a bottomed hole that is coaxially recessed in each of the parallel surfaces 8 c of the lug member 8. The bottom surface of the insertion hole 8e reaches the vicinity of the flow path 6a, but is not in communication with the flow path 6a.

  According to the third embodiment, in addition to the same effects as the first and second embodiments, the flow path 6a and the insertion hole 8e are not in communication with each other, so that the refrigerant gas and the lubricating oil in the flow path 6a Does not leak to the insertion hole 8e side, and the smoothness of the flow of the refrigerant gas and the lubricating oil can be ensured.

  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, in the first to third embodiments, the lug side axis A1 and the central axis A3 of the drive shaft 6 are in a positional relationship where they intersect with each other on the same plane, but according to the present invention, the lug side axis A1 and the drive shaft It is possible to adopt a configuration in which the center axis A3 of 6 intersects on mutually different planes but is in a close positional relationship (positional relationship of torsion).

  Moreover, although the said compressor used the flow path 6a of the drive shaft 6 as the extraction passage, the compressor of this invention may use the flow path 6a of the drive shaft 6 as an air supply path.

  Any motion converting mechanism may be employed as long as it is provided between the swash plate 11 and the piston 13 and converts the swinging motion of the swash plate 11 into the reciprocating motion of the piston 13. it can. Further, the lug member 8 may be integrated with the thrust plate 9.

  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 main part of a compressor according to a first embodiment. 1 is a schematic cross-sectional view of a main part related to a compressor of Example 1. FIG. 1 is a schematic longitudinal sectional view of a drive shaft according to a compressor of Example 1. FIG. FIG. 3 is a schematic side cross-sectional view of the main part of the compressor according to the first embodiment. FIG. 6 is a schematic side cross-sectional view of a main part related to the compressor of Example 2. FIG. 10 is a schematic side cross-sectional view of a main part of a modified example related to the compressor of Example 2. FIG. 6 is a schematic side cross-sectional view of a main part related to the compressor of Example 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)
6 ... Drive shaft 8 ... Lug member 11 ... Swash plate 12 ... Link mechanism 13 ... Piston 11a, 13a, 14 ... Motion conversion mechanism (11a ... Shoe sliding surface, 13a ... Shoe receiving surface, 14 ... Shoe)
11b ... Swash plate arm 20 ... Intermediate arm 21 ... First intermediate arm 22 ... Second intermediate arm 23, 23g, 23k ... Lug side pin 24 ... Swash plate side pin 6a ... Flow path 23b ... Escape part (23b ... Small diameter part, 23c ... Relief space)

Claims (3)

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,
A channel extending in the axial direction is formed in the drive shaft,
The variable-capacity swash plate compressor, wherein the lug-side pin is provided in the vicinity of the central axis of the drive shaft while having an escape portion that avoids the flow path.   The variable displacement swash plate compressor according to claim 1, wherein the escape portion is a small diameter portion formed on the lug side pin.   The variable displacement swash plate compressor according to claim 1, wherein the escape portion is a relief space formed by dividing the lug-side pin.

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