JP2009062856A - Swash plate type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a swash plate type compressor capable of preventing a power loss due to the corotation of the swash plate under a high durability. <P>SOLUTION: The swash plate type compressor of this invention comprises a thrust bearing 20 and a radial bearing 21 preventing corotation of the swash plate with a drive shaft 13 between the swash plate and a rotary plate 17. The swash plate 22 has a recesses 22e formed by indenting a peripheral surface, and pistons 14 are fitted to the recesses 22e. Accordingly, the swash plate 22 and the pistons 14 engage with each other and the swash plate 22 is made irrotational. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a swash plate compressor.

  Conventionally, a swash plate compressor disclosed in Patent Document 1 has been disclosed. 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 on the front housing. A piston is accommodated in each cylinder bore so as to be able to reciprocate, and each piston forms a compression chamber in the cylinder bore.

  A bush that rotates synchronously with the drive shaft is provided in the crank chamber, and a cylindrical peripheral surface having an axis inclined with respect to the axis of the drive shaft is formed on the bush. A swash plate is provided on the peripheral surface of the bush via a radial bearing. A pair of shoes are provided between the front and rear surfaces of the swash plate and the seating surface of each piston. Each shoe has a substantially hemispherical shape. The swash plate is formed with a recess capable of accommodating each shoe on the plane side.

  In this compressor, when the bush rotates as the drive shaft is driven, the swash plate performs only the oscillating motion by the action of the radial bearing. The swinging motion of the swash plate is converted into the reciprocating motion of the piston by the shoe, whereby the refrigerant gas is sucked into the compression chamber from the suction chamber, and the refrigerant gas is compressed and then discharged into the discharge chamber. In the meantime, in this compressor, since the radial bearing is provided between the bush and the swash plate and the shoe is accommodated in the recess of the swash plate, the swash plate prevents the so-called accompanying rotation that tries to rotate with the bush. It is possible. Thus, this compressor prevents power loss.

  A compressor disclosed in Patent Document 2 is also disclosed. In this compressor, a cam member that rotates in synchronization with a drive shaft is provided in a crank chamber, and a cylindrical peripheral surface having an axis inclined with respect to the axis of the drive shaft is formed on the cam member. A swash plate is provided on the back and peripheral surfaces of the cam member via a thrust bearing and a radial bearing, respectively. A plate-like anti-rotation member is fixed to the swash plate by two screws, and the anti-rotation member is formed with a notch capable of accommodating each shoe on the plane side. Other configurations are the same as those of the compressor disclosed in Patent Document 1.

  Also in this compressor, when the cam member rotates as the drive shaft is driven, the swash plate performs only the swinging motion by the action of the thrust bearing and the radial bearing. The swinging motion of the swash plate is converted into the reciprocating motion of the piston by the shoe. During this time, in this compressor, a thrust bearing and a radial bearing are provided between the cam member and the swash plate, and the shoe is housed in the notch of the detent member fixed to the swash plate. It is possible to prevent the accompanying rotation that tries to rotate together with the member. Other operations are the same as those of the compressor disclosed in Patent Document 1.

JP 10-159723 A JP 2001-211151 A

  However, in both compressors, the peripheral edge of the thin shoe is likely to interfere with the recess and the notch, and there is a concern about durability due to deformation of the shoe, the swash plate, or the rotation preventing member.

  The present invention has been made in view of the above-described conventional situation, and as a problem to be solved, to provide a swash plate compressor capable of preventing power loss due to rotation of a swash plate under high durability. Yes.

A swash plate compressor according to the present invention includes a housing having a cylinder bore, a drive shaft rotatably supported by the housing, a piston reciprocally accommodated in the cylinder bore, and the drive shaft and the piston. A swash plate provided between the swash plate for oscillating its own surface by the rotational movement of the drive shaft, and provided between the front and rear surfaces of the swash plate and the seating surface of the piston, A pair of shoes for converting the piston into a reciprocating motion of the piston,
The swash plate has a bearing that avoids rotational movement of the drive shaft,
The swash plate and the piston are engaged with each other to prevent the swash plate from rotating.

  In the compressor of the present invention, in consideration of the fact that the piston cannot reciprocate in the cylinder bore and rotate in the rotation direction of the drive shaft, the swash plate and the piston are directly engaged with each other without a shoe. This prevents the swash plate from being rotated. For this reason, the shoe is not deformed and exhibits excellent durability.

  Therefore, according to the swash plate compressor of the present invention, it is possible to prevent power loss due to rotation of the swash plate under high durability.

  In the swash plate compressor of the present invention, the engaging portion that is a portion for engaging the swash plate and the piston may be a separate member from the swash plate or the piston, or may be integral with the swash plate or the piston. When the engaging portion is integrated with the swash plate, it is preferable that the strength of the swash plate is not concerned as in Patent Document 1 described above. In addition, when the engaging portion is a separate member from the swash plate, the number of parts increases as in Patent Document 2, and the manufacturing cost of the compressor may increase. It is sufficient that the engaging portion is provided for at least one piston. Further, the engagement portion may be less than the thickness of the swash plate.

  Between the drive shaft and the swash plate, there can be provided a rotating plate provided with a bearing between the drive shaft and the swash plate. In this case, the compression reaction force acting on the swash plate can be received by the bearing provided between the rotating plate and the swash plate, and higher durability can be exhibited. If the tilt angle can be changed while the rotating plate rotates synchronously with the drive shaft, a so-called two-swash plate type compressor is obtained.

  As a specific means of the present invention, the swash plate may have a recess having a recessed peripheral surface, and the piston may be fitted into the recess or the recess. Further, as another specific means of the present invention, the swash plate may have a convex portion for projecting the peripheral surface, and the piston may be fitted to the convex portion.

  When the swash plate is provided with a convex portion, the piston is provided with a pair of the shoe and the convex portion as long as the swash plate is configured to be able to change an inclination angle formed with a virtual plane perpendicular to the drive shaft. It is preferable that a spherical guide portion for guiding is formed. In this case, in the piston, since a simple improvement of the conventional seating surface that guides only a pair of shoes can be used as the guide portion, the manufacturing cost can be reduced.

  Embodiments 1 to 4 embodying the present invention will be described below with reference to the drawings.

As shown in FIG. 1, the swash plate compressor according to the first embodiment is of a variable capacity type using CO ₂ as a refrigerant, and a cylinder block 1, a front housing 2, and a rear housing 3 constitute a housing. The cylinder block 1 is provided with a plurality of cylindrical cylinder bores 1a extending in parallel with the axis of the drive shaft 13. In FIG. 1, the left side is the front of the compressor and the right side is the rear of the compressor.

  The rear housing 3 is formed with a suction chamber 5 and a discharge chamber 6 that communicate with each cylinder bore 1a via a valve unit 4. A crank chamber 7 is formed by the front housing 2 and the cylinder block 1, and shaft holes 2 a and 1 b are formed in the front housing 2 and the cylinder block 1. A radial bearing 8 and a shaft seal device 9 are provided in the shaft hole 2a, a radial bearing 10 and a thrust bearing 11 are provided in the shaft hole 1b, and a pressing spring 12 is provided between the thrust bearing 11 and the valve unit 4. It has been. The drive shaft 13 is rotatably supported by the radial bearing 8 or the like with one end protruding from the front housing 2. A piston 14 is accommodated in each cylinder bore 1a so as to be able to reciprocate, and each piston 14 forms a compression chamber in the cylinder bore 1a.

  A lug plate 15 is fixed to the drive shaft 13 in the crank chamber 7, and a thrust bearing 16 is provided between the lug plate 15 and the front housing 2. The drive shaft 13 is inserted with a rotating plate 17 capable of changing an inclination angle formed with a virtual plane perpendicular to the drive shaft 13. A link mechanism 18 is provided between the lug plate 15 and the rotating plate 17, and a pressing spring 19 that biases the lug plate 15 and the rotating plate 17 in a direction away from the lug plate 15 is provided. A swash plate 22 is provided on the back surface of the rotary plate 17 via a thrust bearing 20 and a radial bearing 21.

  Further, shoes 23 a and 23 b are provided between the rotary plate 17 and the swash plate 22 and each piston 14. The shoe 23 a is provided between the surface of the rotating plate 17 and the front seat surface 14 a of the piston 14, and the shoe 23 b is provided between the surface of the swash plate 22 and the rear seat surface 14 b of the piston 14. . Each shoe 23a, 23b is substantially hemispherical. Thus, this compressor is a so-called two-swash plate type, and the durability is improved by employing the shoes 23a and 23b.

  A capacity control valve 24 is accommodated in the rear housing 3. The capacity control valve 24 communicates with the suction chamber 5 through the detection passage 3a, and communicates the discharge chamber 6 with the crank chamber 7 through the air supply passage 3b. The capacity control valve 24 detects the pressure in the suction chamber 5 to change the opening of the air supply passage 3b and change the discharge capacity of the compressor. The crank chamber 7 and the suction chamber 5 are communicated with each other through an extraction passage 1c. A condenser 26, an expansion valve 27 and an evaporator 28 are connected to the discharge chamber 6 by a pipe 25, and the evaporator 28 is connected to the suction chamber 5 by a pipe 25. The drive shaft 13 is operatively connected to an engine E as an external drive source that is also a travel drive source of the vehicle via a power transmission mechanism PT formed of an electromagnetic clutch or a pulley.

  Each piston 14 includes a cylindrical main body 14c that forms a compression chamber on the head side, and a neck portion 14d that is integral with the main body 14c on the swash plate 22 side. The neck portion 14d is formed with a recess 14e that opens toward the drive shaft 13 and accommodates the rotating plate 17, the thrust bearing 20, the swash plate 22, and the pair of shoes 23a and 23b. A seat surface 14a that receives the spherical surface of the shoe 23a is formed on the neck portion 14d in front of the recess 14e, and a seat surface 14b that receives the spherical surface of the shoe 23b is formed on the neck portion 14d on the rear side of the recess 14e. The seating surfaces 14a and 14b constitute the outer surface of the same sphere.

  As shown in FIGS. 2 and 3, the peripheral surface of the swash plate 22 is provided with the same number of recesses 22 e as the number of pistons 14. Each piston 14 has a neck portion 14d fitted in each recess 22e.

  In the compressor configured as described above, the lug plate 15 and the rotating plate 17 rotate synchronously when the drive shaft 13 rotates. When the rotating plate 17 rotates, relative rotation occurs between the rotating plate 17 and the swash plate 22 by the action of the thrust bearing 20 and the radial bearing 21, and the rotation speed of the swash plate 22 is lower than the rotation speed of the rotating plate 17. To do. The swinging motion of the rotating plate 17 and the swash plate 22 is converted into the reciprocating motion of the piston 14 by the shoes 23a and 23b. As a result, the volume of the compression chamber changes. Therefore, the refrigerant gas in the suction chamber 5 is sucked into the compression chamber and compressed, and then discharged into the discharge chamber 6. In this way, the refrigeration operation is performed in the refrigeration circuit including the compressor, the condenser 26, the expansion valve 27, and the evaporator 28.

  If the capacity control valve 24 changes the pressure in the crank chamber 7, the link mechanism 18 allows the angle variation of the rotating plate 17 and the swash plate 22 to the lug plate 15, and the discharge capacity of the compressor is changed. .

  During this time, each piston 14 does not reciprocate in the cylinder bore 1a and rotate in the rotational direction of the drive shaft 13. The swash plate 22 is directly engaged with the pistons 14 without using the shoes 23a and 23b. In this way, the rotation of the swash plate 22 is prevented. For this reason, this compressor does not deform the shoes 23a and 23b unlike the conventional compressor, and exhibits excellent durability.

  Therefore, according to this compressor, power loss due to rotation of the swash plate 22 can be prevented with high durability.

  Further, in this compressor, each piston 14 is prevented from rolling by the neck portion 14 d fitting into the recess 22 e of the swash plate 22. For this reason, the neck part 14d does not shake greatly from side to side, and noise due to the neck part 14d interfering with the front housing 2 and the swash plate 22 is also prevented. And since it is not necessary to provide the front housing 2 with the guide surface for rolling prevention of each piston 14, the volume of the crank chamber 7 can be ensured large. For this reason, it is possible to secure a large amount of lubricating oil in the crank chamber 7, and it is possible to eliminate the concern of power loss due to insufficient lubricating oil in the crank chamber 7.

  Further, in this compressor, the swash plate 22 and the pistons 14 are engaged with each other by forming the recesses 22e in the swash plate 22, so that the swash plate 22 is prevented from rotating and the pistons 14 are prevented from rolling. Therefore, another member is not used. For this reason, the cost can be reduced by reducing the number of parts.

  In the compressor according to the first embodiment, the swash plate 22 may be provided with one or more recesses 22e than the number of the pistons 14. Also in this case, it is possible to prevent the swash plate 22 from being rotated.

  In the compressor of the second embodiment, as shown in FIG. 4, a convex portion 22 f protrudes from a part of the peripheral surface of the swash plate 22. Further, the neck portion 14d of one piston 14 is provided with a concave portion 14f that fits the convex portion 22f. Other configurations are the same as those of the first embodiment.

  Also in this compressor, the accompanying rotation of the swash plate 22 can be prevented.

  In the compressor of the second embodiment, the swash plate 22 may be provided with the same number of convex portions 22f as the number of the pistons 14, and the convex portions 22f may be fitted into the concave portions 14f of the pistons 14. In this case, other functions and effects can be obtained in the same manner as in the first embodiment.

  In the compressor according to the third embodiment, as illustrated in FIG. 5, a rotating plate 30 different from the rotating plate 17 according to the first embodiment is inserted through the drive shaft 13. A swash plate 33 is provided on the back surface of the rotating plate 30 via a thrust bearing 31 and a radial bearing 32. Pairs of shoes 23 a and 23 b are provided between the front and rear surfaces of the swash plate 33 and the seating surface of the piston 14.

  Each piston 14 is formed with a guide portion 14g constituting the outer surface of the same sphere as the seating surfaces 14a and 14b. Further, the same number of convex portions 33 a as the number of pistons 14 project from the peripheral surface of the swash plate 33. The outer surface of each convex portion 33a is a part of a spherical surface aligned with the guide portion 14g. Other configurations are the same as those of the first embodiment.

  In the compressor configured as described above, the lug plate 15 and the rotating plate 30 rotate synchronously as the drive shaft 13 rotates. When the rotating plate 30 rotates, the swash plate 33 does not rotate due to the action of the thrust bearing 31 and the radial bearing 32. For this reason, the piston 14 reciprocates in the cylinder bore 1a via the shoes 23a and 23b.

  During this time, also in this compressor, the swash plate 33 is prevented from rotating as in the first and second embodiments. In addition, in this compressor, since the conventional seating surfaces 14a and 14b for guiding only the paired shoes 23a and 23b can be easily improved in each piston 14, the guide portion 14g can be formed. It is also possible to reduce the cost. Other functions and effects are the same as those of the first embodiment.

  In the compressor according to the third embodiment, the swash plate 33 is provided with one or fewer projections 33a than the number of the pistons 14, and the piston 14 having the guide portions 14g fitted to these or these projections 33a is employed. It is also possible. Also in this case, the rotation of the swash plate 33 can be prevented.

  As shown in FIG. 6, the compressor of the fourth embodiment is of a fixed capacity type, and includes a cylinder block 41, a front housing 42, and a rear housing 43. The cylinder block 41 includes a plurality of housings. A cylinder bore 41a is provided therethrough. In FIG. 6, the left side is the front of the compressor, and the right side is the rear of the compressor.

  The rear housing 43 is formed with a suction chamber 45 and a discharge chamber 46 that communicate with the cylinder bores 41 a via a valve unit 44. A crank chamber 47 is formed by the front housing 42 and the cylinder block 41, a shaft hole 42 a is formed in the front housing 42, and a shaft hole 41 b is recessed in the cylinder block 41. A thrust bearing 48 and a shaft seal device 49 are provided in the shaft hole 42a, a radial bearing 50 and a thrust bearing 51 are provided in the shaft hole 41b, and a pressing spring 52 is provided between the thrust bearing 51 and the bottom surface of the shaft hole 41b. Is provided. The drive shaft 53 is rotatably supported by the thrust bearing 48 or the like with one end protruding from the front housing 42. A piston 54 is accommodated in each cylinder bore 41a so as to be able to reciprocate, and each piston 54 forms a compression chamber in the cylinder bore 41a.

  In the crank chamber 47, a thrust plate 55 is fixed to the drive shaft 53, and a thrust bearing 48 is provided between the thrust plate 55 and the front housing 42. A cylindrical inclined portion 55 a having an axis inclined with respect to the axis of the drive shaft 53 is integrally formed on the rear side of the thrust plate 55. A swash plate 58 is provided on the peripheral surface of the inclined portion 55 a via a thrust bearing 56 and a radial bearing 57. A pair of shoes 23 a and 23 b are provided between the front and rear surfaces of the swash plate 58 and the seating surface of the piston 54.

  Each piston 54 is formed with a guide portion 14g constituting the outer surface of the same sphere as the seating surfaces 14a and 14b. Further, the same number of protrusions 33 a as the number of pistons 54 protrude from the peripheral surface of the swash plate 58. The outer surface of each convex portion 33a is a part of a spherical surface aligned with the guide portion 14g. Other configurations are the same as those of the third embodiment.

  In the compressor configured as described above, the thrust plate 55 rotates synchronously as the drive shaft 53 rotates, and the swash plate 58 does not rotate due to the action of the thrust bearing 56 and the radial bearing 57. For this reason, the piston 54 reciprocates in the cylinder bore 41a via the shoes 23a and 23b. Also in this compressor, the same operation effect as Example 3 can be produced.

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

  For example, in the compressors according to the first to fourth embodiments, it is possible to provide a guide surface on the housing in order to prevent the pistons 14 and 54 from rolling.

  The present invention is applicable to a vehicle air conditioner.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a variable capacity swash plate compressor according to a first embodiment. 1 is a cross-sectional view of a main part of a variable displacement swash plate compressor according to a first embodiment. FIG. 3 is an enlarged cross-sectional view of a main part of the variable capacity swash plate compressor according to the first embodiment. FIG. 5 is an enlarged cross-sectional view of a main part of a variable capacity swash plate compressor according to a second embodiment. FIG. 6 is a longitudinal sectional view of a variable capacity swash plate compressor according to a third embodiment. 6 is a longitudinal sectional view of a fixed capacity swash plate compressor according to Embodiment 4. FIG.

Explanation of symbols

1a, 41a ... cylinder bores 1, 2, 3, 41, 42, 43 ... housing (1, 41 ... cylinder block, 2, 42 ... front housing, 3, 43 ... rear housing)
13, 53 ... Drive shaft 14, 54 ... Piston 22, 33, 57 ... Swash plate 23a, 23b ... Shoe 20, 21, 31, 32, 56, 57 ... Bearing (20, 31, 56 ... Thrust bearing, 21, 32 57 ... Radial bearings)
17, 30 ... Rotating plate 22e ... Concave part 22f ... Convex part 14g ... Guide part

Claims (5)

A housing having a cylinder bore; a drive shaft rotatably supported by the housing; a piston reciprocally accommodated in the cylinder bore; and a drive shaft provided between the piston and the drive shaft. A swash plate that oscillates its surface by a rotational motion, and is provided between the front and back surfaces of the swash plate and the seat surface of the piston, and converts the oscillating motion of the swash plate into a reciprocating motion of the piston. With a pair of shoes,
The swash plate has a bearing that avoids rotational movement of the drive shaft,
The swash plate compressor, wherein the swash plate and the piston engage with each other to prevent the swash plate from rotating.   The swash plate type compressor according to claim 1, further comprising a rotary plate provided with the bearing between the drive shaft and the swash plate.   The swash plate compressor according to claim 1 or 2, wherein the swash plate has a concave portion having a concave peripheral surface, and the piston is fitted in the concave portion.   The swash plate compressor according to claim 1 or 2, wherein the swash plate has a convex portion for projecting a peripheral surface, and the piston is fitted to the convex portion.   The swash plate is configured to change an inclination angle formed with a virtual plane perpendicular to the drive shaft, and the piston is formed with a spherical guide portion for guiding the pair of shoes and the convex portion. The swash plate compressor according to claim 4.

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