JP2010084588A - Compressor pulley structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor which can demonstrate stable sealing performance without being affected by centrifugal force. <P>SOLUTION: The compressor pulley structure of the compressor 1 which compresses a coolant by a swash plate 15 fixed to a rotary shaft 20 is provided with a driven pulley 50, an electromagnetic clutch 24, and a bearing 40. The driven pulley 50 over which a power transmission member is looped transmits the power of an external driving source to the rotary shaft 20, and the electromagnetic clutch 24 performs disengagement/engagement of power transmission between the driven pulley 50 and the rotary shaft 20. The bearing 40 supports the driven pulley 50 to a compressor body 10 with possible rotation, and a sealing ring 127 is engaged with the outer ring 121 of the bearing 40. The inner ring 120 of the bearing 40 is fixed to the driven pulley 50, and the outer ring 121 is fixed to the compressor body 10. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a compressor pulley structure of a compressor constituting an air conditioner for an automobile.

  For example, compressors of various structures are conventionally known as compressors that compress refrigerant by incorporating it into a vapor compression refrigerator incorporated in an air conditioner for automobiles. For example, Patent Document 1 describes a swash plate type compressor that converts the rotational movement of a rotary shaft into a reciprocating movement of a piston by a swash plate and compresses the refrigerant by the piston. FIG. 3 shows a swash plate type compressor described in Patent Document 1. The structure shown in FIG. 3 is a variable displacement swash plate compressor of which the capacity can be adjusted by changing the inclination angle of the swash plate among the conventionally known swash plate compressors.

  The compressor 100 causes the plurality of pistons 104 to reciprocate within the cylinders 105 as the swash plate 103 rotates together with the rotating shaft 102. As the piston 104 reciprocates, the refrigerant vapor in the low-pressure chamber 107 communicating with the suction port 106 is sucked into the cylinder 105. Next, the refrigerant vapor is compressed in the cylinder 105 and then sent out to the high-pressure chamber 108. Further, by adjusting the pressure in the crank chamber 110 where the swash plate 103 exists and the low pressure chamber 107 according to the cooling load, and changing the inclination angle of the swash plate 103, the capacity of the compressor 100 is changed. To change.

  The rotating shaft 102 of the compressor 100 configured as described above is rotationally driven by, for example, an automobile traveling engine. For this reason, in the case of the illustrated example, a driven pulley 113 is rotated by a rolling bearing 114 around a support cylinder portion 112 provided at the center of the outer surface (the left side surface in FIG. 3) of the casing 110 constituting the compressor 100. Supports freely. The driven pulley 113 has a U-shaped cross section and is formed in an annular shape as a whole. A solenoid 115 fixed to the outer surface of the casing 110 is disposed in the internal space of the driven pulley 113. The solenoid 115, the annular plate 117, and the leaf spring 118 constitute an electromagnetic clutch 119 for opening and closing the driven pulley 113 and the rotating shaft 102.

  As shown in FIG. 4, the rolling bearing 114 that supports the driven pulley 113 includes an inner ring 120, an outer ring 121, and a plurality of rolling elements 122. Of these, the inner ring 120 is externally fitted and fixed to a fixed portion such as the support cylinder 112 and does not rotate during use. An inner ring raceway 123 is formed on the outer peripheral surface of the inner ring 120. The outer ring 121 is fitted with a driven pulley 113 (see FIG. 3) on the outer peripheral surface, and rotates together with the driven pulley 113 during use. An outer ring raceway 124 is formed on the inner peripheral surface of the outer ring 121. Each rolling element 122 held by the retainer 125 is provided between the inner ring raceway 123 and the outer ring raceway 124 so as to roll freely.

  Further, on the inner peripheral surface of the outer ring 121, in order to prevent leakage of grease sealed in the internal space of the rolling bearing 114, seal rings 127 are provided at both axial end openings of the internal space. Each of these seal rings 127 is formed in an annular shape, and its outer peripheral edge is locked to a locking groove 128 formed on the inner peripheral surface of both end portions in the axial direction of the outer ring 121. Further, seal lips 129 a and 129 b are formed on the inner peripheral edge of each seal ring 127, and the inner peripheral surface of the seal lip 129 a formed so as to protrude inward in the axial direction is used as the outer periphery of the inner ring 120. The shoulder portion 130 formed on the surface is closely opposed. Further, the seal lip 129 b formed on the inner peripheral edge of the seal ring 127 is brought into sliding contact with a part of the seal groove 131 formed on the outer peripheral surface of both ends of the inner ring 120 on the outer side in the axial direction from the shoulder portion 130.

In this way, the seal ring 127 closes the openings at both ends of the internal space, thereby preventing leakage of grease sealed in the internal space, and foreign matters such as dust floating outside enter the internal space. To prevent it. That is, among the seal lips 129 a and 129 b formed on the inner peripheral edge of the seal ring 127, the seal lip 129 a that protrudes inward in the axial direction is placed close to and opposed to the shoulder portion 130, thereby being enclosed in the internal space of the rolling bearing 114. Prevents leakage of grease. Further, the seal lip 129b is brought into sliding contact with a part of the seal groove 131, thereby preventing foreign matter from entering the internal space.
JP 2003-278774 A

  However, in the compressor 100 described in Patent Document 1, in the rolling bearing 114, the driven pulley 113 is fixed to the outer ring 121, and the support cylinder portion 112 provided at the center of the outer surface of the casing 110 constituting the compressor 100 is fixed to the inner ring 120. Therefore, the rolling bearing 114 is used for rotating the outer ring. In recent years, with the increase in the operating speed of the compressor, the rotational speed of the driven pulley 113 and the outer ring 121 that externally engages the driven pulley 113 also increases, and the outer ring 121 rotates at a high speed, so that the seal ring 127 vibrates. As a result, the grease enclosed in the internal space tends to leak easily.

  Further, since the seal ring 127 locked to the outer ring 121 also rotates together with the outer ring 121, there is a possibility that centrifugal force acts on the seal lips 129a and 129b that are in sliding contact with the outer peripheral surface of the inner ring 120, and reliable sealing performance cannot be exhibited. there were.

  Further, in the rolling bearing 114 used for rotating the outer ring, the outer ring 121 and the driven wheel of the rolling bearing 114 are driven by the moment force M generated by the pressing force F applied to the driven pulley 113 of the annular plate 117 when the electromagnetic clutch 119 is operated. There may be a gap between the inner diameter portion 116 of the pulley 113. This gap causes a slip between the rolling bearing 114 and the driven pulley 113, and if metal dust or the like attracted by the electromagnetic clutch 119 enters the gap, the driven pulley 113 rotates during long-term use. It was difficult to maintain the accuracy with respect to the roundness.

  The present invention has been made to eliminate such inconveniences, and an object of the present invention is to provide a compressor pulley structure that can exhibit stable sealing performance without being affected by centrifugal force. .

  The object of the present invention is to provide a compressor pulley structure of a compressor that compresses refrigerant by a compression rotator fixed to a rotating shaft, and a power transmission member is stretched over to transmit the power of an external drive source to the rotating shaft. A pulley, an electromagnetic clutch that releases and fastens power transmission between the pulley and the rotating shaft, and a bearing that rotatably supports the pulley with respect to a compressor body and in which a seal member is locked to an outer ring. And the inner ring of the bearing is fixed to the pulley, and the outer ring is fixed to the compressor body.

  According to the compressor pulley structure of the present invention, the inner ring of the bearing is fixed to the pulley, and the outer ring is fixed to the compressor body. Therefore, since the sealing member locked to the outer ring does not rotate, it is possible to exhibit stable sealing performance without being affected by centrifugal force.

  Usually, the contact surface pressure between the ball and the inner ring raceway surface is higher than the contact surface pressure between the ball and the outer ring raceway surface. However, when the outer ring rotates, one point on the inner ring raceway surface where the surface pressure is high is the maximum load position. However, in the inner ring rotation, the inner ring with high surface pressure supports the load on the entire circumference of the raceway surface, and the load is supported at one point on the outer ring raceway surface with low surface pressure.

  Hereinafter, a compressor for a car air conditioner as an embodiment of a compressor having a compressor pulley structure according to the present invention will be described in detail with reference to the drawings.

  As shown in FIG. 1, a compressor (compressor) 1 as an example of a car air conditioner compressor includes a casing 11 in a compressor main body (compressor main body) 10, and pistons 13 can be reciprocated in a plurality of cylinders 12, respectively. The swash plate 15 (compression rotator) is slidably sandwiched between the opposed half-moon shaped shoes 14 and 14 provided on the piston base, and the piston 13 is reciprocated by rotating the swash plate 15. Yes.

  A pin 18 provided at an end of the arm 17 fixed to the swash plate 15 is fitted into a long hole 22 provided in a rotary drive member 21 that rotates integrally with the rotary shaft 20 and has a spherical surface. 23 is fitted to the rotary shaft 20, and the sleeve 23 is urged in the axial direction by a spring 25, and the swash plate 15 is rotatably supported on the outer periphery of the sleeve 23.

  The compressor 1 shown in FIG. 1 includes an electromagnetic clutch 24, a leaf spring 28 is fixed to a mounting bracket 26 provided at the end of the rotating shaft 20, and an annular plate made of a magnetic material at the outer peripheral tip of the leaf spring 28. 29 is fixed. In the illustrated embodiment, a driven pulley 50 having a U-shaped cross section is supported via a bearing 40 on a support cylinder portion 32 protruding from an end casing 30 of the compressor 1.

  The driven pulley 50 includes a pulley portion 51 around which an endless belt as a power transmission member is stretched, an inner diameter side cylindrical portion 52 that is located on the inner diameter side of the pulley portion 51 and faces the support cylinder portion 32 via the bearing 40, and a pulley The annular plate portion 53 that connects the portion 51 and the inner diameter side cylindrical portion 52 is configured to have a U-shaped cross section.

  A solenoid 35 fixed to the end casing 30 side is disposed in the U-shaped space in the cross section, and the magnetic material is disposed at a position facing the solenoid 35 with the annular plate portion 53 of the driven pulley 50 interposed therebetween. An annular plate 29 is arranged. The bearing 40 is usually a compressor pulley bearing having an outer diameter of 65 mm or less, and has a sealing function of enclosing grease inside.

  The bearing 40 is a double row ball bearing, and will be described below with reference to the rolling bearing 114 (double row ball bearing) of FIG. 4 having the same configuration. The bearing 40 exists between the outer peripheral surface of the inner ring 120 and the inner peripheral surface of the outer ring 121 and encloses grease in an internal space in which the respective rolling elements 122 are installed, and the rolling surfaces of the respective rolling elements 122 and the inner ring raceway 123 are sealed. And the outer ring raceway 124 is lubricated.

  Sealing rings (seal members) 127 are respectively provided at openings in both ends in the axial direction of the internal space. Each of these seal rings 127 is formed in a ring shape, and the outer peripheral edge portion is the inner peripheral surface of both ends in the axial direction of the outer ring 121. It is locked in the locking groove 128 formed in the above. Further, seal lips 129 a and 129 b are formed on the inner peripheral edge of each seal ring 127, and the inner peripheral surface of the seal lip 129 a formed so as to protrude inward in the axial direction is used as the outer periphery of the inner ring 120. The shoulder portion 130 formed on the surface is closely opposed. Further, the seal lip 129 b formed on the inner peripheral edge of the seal ring 127 is brought into sliding contact with a part of the seal groove 131 formed on the outer peripheral surface of both ends of the inner ring 120 on the outer side in the axial direction from the shoulder portion 130.

  In this way, the seal ring 127 closes the openings at both ends of the internal space, thereby preventing leakage of grease sealed in the internal space, and foreign matters such as dust floating outside enter the internal space. To prevent it. That is, of the seal lips 129a and 129b formed on the inner peripheral edge of the seal ring 127, the seal lip 129a protruding inward in the axial direction is brought close to and opposed to the shoulder portion 130, whereby the grease sealed in the internal space leaks out. To prevent things. Further, the seal lip 129b is brought into sliding contact with a part of the seal groove 131, thereby preventing foreign matter from entering the internal space.

  In the electromagnetic clutch 24 shown in FIG. 1, the annular plate 29 is separated from the annular plate portion 53 of the driven pulley 50 as shown in the figure when the solenoid 35 is not energized, and even if the driven pulley 50 is rotated by the endless belt. The annular plate 29 does not rotate and therefore the compressor 1 does not operate. On the other hand, when the solenoid 35 is energized, the annular plate 29 made of a magnetic material is attracted by the magnetic force, and the annular plate 29 is pressed against the annular plate portion 53 of the driven pulley 50. As a result, the electromagnetic clutch 24 is engaged, and when the driven pulley 50 is rotated, the annular plate 29 is also rotated integrally, and the swash plate 15 is rotated through the leaf spring 28, the mounting bracket 26, and the rotating shaft 20 as described above. The compressor 1 is operated by reciprocating the piston 13. In this way, the electromagnetic clutch 24 releases and fastens power transmission between the driven pulley 50 and the rotary shaft 20.

  The compressor 1 configured in this manner reciprocates the plurality of pistons 13 in the cylinder 12 by the rotation of the swash plate 15 together with the rotary shaft 20. As the piston 13 reciprocates, the refrigerant vapor in the low-pressure chamber 7 leading to the suction port 26 is sucked into the cylinder 12. Next, the refrigerant vapor is compressed in the cylinder 12 and then sent out to the high-pressure chamber 28. Further, by adjusting the pressure of the crank chamber 60 where the swash plate 15 exists and the low pressure chamber 27 by the pressure adjusting valve 29 according to the cooling load, and changing the inclination angle of the swash plate 15, the capacity of the compressor 1 is changed. Can be changed.

  Here, in the pulley structure of the compressor 1 of the present invention, the inner ring 120 of the bearing 40 is fixed to the driven pulley 50, and the outer ring 121 is fixed to the compressor body 10. More specifically, as shown in FIGS. 1 and 2, the inner ring 120 of the bearing 40 is fitted on the inner diameter side cylindrical portion 52 of the driven pulley 50 and rotates together with the driven pulley 50, while the outer ring 121 has an end casing. It is fitted and fixed to the support cylinder part 32 protruding from 30.

  Therefore, according to the pulley structure of the compressor 1 of the present invention, the inner ring 120 of the bearing 40 is fitted onto the inner diameter side cylindrical portion 52 of the driven pulley 50, and the outer ring 121 is fitted into the support cylinder portion 32 protruding from the end casing 30. Since it is fitted, the bearing 40 is used for inner ring rotation. Therefore, since the seal ring 127 locked to the outer ring 121 does not rotate, it is possible to exhibit stable sealing performance without being affected by centrifugal force.

  In general, the contact surface pressure between the ball and the inner ring raceway surface is higher than the contact surface pressure between the ball and the outer ring raceway surface, and one point of the inner ring raceway surface having a higher surface pressure is the maximum load position when the outer ring rotates. However, according to the compressor 1 of the present invention, the inner ring 120 having a high surface pressure supports a load on the entire circumference of the raceway surface, and the outer ring raceway surface 124 having a low surface pressure has one point because it is used for inner ring rotation. As a result, the bearing 40 is supported for a long life, which contributes to a long life of the compressor 1.

  Further, in the bearing 40 used for rotating the inner ring, the moment force M generated by the pressing force F applied to the driven pulley 50 of the annular plate 29 during the operation of the electromagnetic clutch 24 causes the bearing 40 to move to the inner cylindrical portion 52. It acts so as to be sandwiched between the support cylinder portion 32. Accordingly, no gap is generated between the inner ring 120 and the inner diameter side cylindrical portion 52 and between the outer ring 121 and the support cylinder portion 32 when the electromagnetic clutch 24 is operated. Therefore, the accuracy can be maintained with respect to the roundness of the rotation of the driven pulley 50 even in long-term use.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. For example, the bearing 40 may be a single row ball bearing shown in FIG. 2 and is not particularly limited to these structures. However, in the case of a single-row ball bearing, it is preferable to consider a three-point or four-point contact type to support the moment load acting from the driven pulley 50. In addition, the material, shape, dimension, numerical value, form, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

It is sectional drawing of the compressor for car air conditioners provided with the pulley structure of one Embodiment of this invention. It is principal part sectional drawing which shows the modification of the compressor for car air conditioners. 2 is a cross-sectional view of a car air conditioner compressor described in Patent Document 1. FIG. It is principal part sectional drawing of the rolling bearing integrated in the compressor for car air conditioners of FIG.

Explanation of symbols

1 Compressor
10 Compressor body (Compressor body)
15 Swash plate (compression rotating body)
20 Rotating shaft 24 Electromagnetic clutch 40 Bearing 50 Driven pulley (pulley)
120 Inner ring 121 Outer ring 127 Seal ring (seal member)

Claims (1)

In the compressor pulley structure of the compressor that compresses the refrigerant by the compression rotating body fixed to the rotating shaft,
A pulley over which a power transmission member is stretched and transmitting the power of an external drive source to the rotating shaft;
An electromagnetic clutch for releasing and fastening power transmission between the pulley and the rotating shaft;
A bearing that rotatably supports the pulley with respect to the compressor body, and a seal member that is locked to the outer ring.
A compressor pulley structure, wherein an inner ring of the bearing is fixed to the pulley, and the outer ring is fixed to the compressor body.

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