JP2006132423A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor enabling a reduction in weight by partly using light-weight members therefor. <P>SOLUTION: This compressor comprises a housing 1 having, therein, a crankcase 5, a suction chamber 7, a discharge chamber 8, and a cylinder bore 3, a drive shaft 10 rotatably pivoted on the housing 1 and rotatingly driven in the crankcase 5, a rotating member 21 press-fitted to the drive shaft 10, a piston 29 reciprocatingly moving in the cylinder bore 3 by utilizing the rotation of the rotating member 21 and sucking, compressing, and discharging a compressed medium by the reciprocating motion, and a rotation stop member 38 fixedly holding the rotating member 21 on the drive shaft 10 integrally with each other. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compressor, and more particularly to a compressor suitable for a compressor that is interposed in a refrigeration cycle such as a vehicle air conditioner.

For example, Patent Documents 1 to 4 disclose a compressor. In recent years, this type of compressor is required to be smaller and lighter. This is because, for example, it is a problem to reduce the size and weight of the on-vehicle equipment for the reason of widening the living space in a vehicle such as an automobile.
JP-A-2003-328931 JP-A 61-255285 JP-A-5-231309 JP 2002-213350 A

  From the viewpoint of reducing the weight of such a compressor, the present inventor has conceived that a lightweight member is partially used in addition to a member that requires rigidity and strength, such as a drive shaft.

  By the way, generally, when the compressor is operated, the internal temperature rises due to the compression heat of the medium to be compressed. Therefore, in a portion where different materials are press-fitted and fixed, when the temperature in the compressor rises, the thermal expansion coefficient is different, so that the fastening margin may change and the fixing may be loosened.

  The present invention has been made based on such a conventional technique, and an object of the present invention is to provide a compressor capable of maintaining the fixed state of the lightweight member while reducing the weight by partially using the lightweight member.

  In the first aspect of the present invention, a housing having a crank chamber, a suction chamber, a discharge chamber, and a cylinder bore therein, a drive shaft that is pivotally supported by the housing and rotationally driven in the crank chamber, A rotary member press-fitted into the drive shaft, a piston that reciprocates in the cylinder bore using the rotation of the rotary member, and a reciprocating motion that sucks, compresses, and discharges the medium to be compressed, and the drive shaft And a rotation preventing member that integrally fixes and holds the rotating member.

  A second aspect of the present invention is the compressor according to the first aspect, wherein a passage communicating with the suction chamber is provided in the drive shaft, and the anti-rotation member is formed of a hollow member having both end openings. The opening is exposed to the crank chamber and the other end opening communicates with the passage.

  A third aspect of the present invention is the compressor according to the first or second aspect, wherein the rotating member is connected to a swash plate for reciprocating the piston and rotates integrally with the drive shaft. Thus, the drive plate swings the swash plate.

  According to the first aspect of the present invention, even if the rotating member is made of a lightweight member, the rotation member can reliably maintain the fixed state of the rotating member with respect to the drive shaft. That is, when the inside of the compressor becomes high temperature due to the compression heat of the medium to be compressed, it is assumed that the tightening changes due to the difference in the thermal expansion coefficient between the rotating member and the drive shaft, and the press-fit is loosened. However, the fixed state of the rotating member and the drive shaft can be reliably maintained by the rotation preventing member. Thus, the weight of the compressor can be reduced by using a lightweight member in part.

  According to the second aspect of the present invention, the hollow passage of the rotation preventing member constitutes the inlet portion of the extraction passage. Therefore, the mist-like oil that tries to flow into the extraction passage together with the refrigerant gas from the crank chamber collides with the inner peripheral surface of the hollow passage of the rotation preventing member as the inlet portion of the extraction passage by the rotational movement of the drive shaft. Be captured. Next, the oil adhering to the inlet portion of the bleed passage is pushed back to the crank chamber by the centrifugal force generated by the rotational movement of the drive shaft. Accordingly, the lubricating oil in the crank chamber is less likely to flow into the suction chamber through the extraction passage, and the amount of oil outflow from the extraction passage can be reduced with a simple configuration.

  In addition to this effect, by setting the axial length of the anti-rotation member, the distance of the inlet portion that becomes the radial passage of the extraction passage can be increased, so that the centrifugal action can be further increased.

  According to the invention described in claim 3, since the rotating member is a drive plate, a relatively large member (drive plate) among the rotating members fixed to the drive shaft can be reduced in weight, and the compressor can be effectively used. Weight can be reduced.

  Hereinafter, specific embodiments to which the present invention is applied will be described in detail with reference to the drawings.

  The present embodiment is an example in which the compressor of the present invention is applied to a refrigeration cycle of a vehicle air conditioner mounted on a vehicle such as an automobile.

  1 to 4 show an embodiment of a compressor according to the present invention, FIG. 1 is a sectional view of the compressor, and FIGS. 2 and 3 are enlarged views of an inlet side of a bleed passage in the compressor of FIG. FIG. 4 is a partial sectional view showing the action of oil separation by the inlet portion of the extraction passage, and FIG. 4 is an enlarged sectional view showing the outlet side of the extraction passage in the compressor of FIG.

  As shown in FIG. 1, the compressor in the present embodiment is a swash plate type variable capacity compressor. This swash plate type variable capacity compressor includes a cylinder block 2 having a plurality of cylinder bores 3, a front housing 4 joined to the front end surface of the cylinder block 2 to form a crank chamber 5 between the cylinder block 2, a cylinder The rear housing 6 is joined to the rear end face of the block 2 via a valve plate 9 and forms a suction chamber 7 and a discharge chamber 8.

  The cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by through bolts to constitute a compressor housing 1.

  The valve plate 9 includes a suction hole 11 that communicates the cylinder bore 3 and the suction chamber 7, and a discharge hole 12 that communicates the cylinder bore 3 and the discharge chamber 8.

  A suction valve (not shown) for opening and closing the suction hole is provided on the cylinder block 2 side of the valve plate 9, while a discharge valve (not shown) for opening and closing the discharge hole 12 is provided on the rear housing 6 side of the valve plate 9. And a retainer 15 that holds the discharge valve and restricts the opening limit of the discharge valve.

    In the central part of the cylinder block 2 and the front housing 4, shaft support holes 19 and 20 are provided for rotatably supporting the drive shaft 10 via bearings 17, 37 and 18.

  In the crank chamber 5, a drive plate 21 as a “rotating member” that is press-fitted and fixed to the drive shaft 10 from the outside, a sleeve 22 that is slidably fitted to the drive shaft 10, and swings on the sleeve 22. A freely connected journal 24 and a swash plate 26 fixed to a boss portion 25 of the journal 24 are provided. At this time, the drive plate 21 is fixed to the drive shaft 10 so as to be surely integrally rotated by a fixing pin 38 as a “rotation preventing member”. The fixing pin 38 is made of a hollow member having openings at both ends.

  The drive plate 21 and the journal 24 have their hinge arms 21h and 24h connected to each other via a link 27 and pins 28 and 28, thereby transmitting the rotational force of the drive plate 21 to the journal 24. The inclination of the (swash plate 26) can be allowed. The pistons 29 accommodated in the cylinder bores 3 are connected to the swash plate 26 via a pair of shoes 30 sandwiching the swash plate 26, and reciprocate using the rotational motion of the drive shaft 10 as a driving force.

  The basic function of the compressor is to compress the refrigerant as the medium to be compressed sucked into the suction hole 7 → the suction hole of the valve plate 9 → the cylinder bore 3 by the reciprocating motion of the piston 29, and the cylinder bore 3 → the valve plate 9. The discharge hole 12 is discharged to the discharge chamber 8.

  In order to make the discharge capacity variable, an extraction passage 31 (shown by an arrow in FIG. 1) that always communicates the crank chamber 5 and the suction chamber 7 and an air supply passage 32 that communicates the crank chamber 5 and the discharge chamber 8. There is provided a pressure control mechanism (shown by an arrow in FIG. 1) and pressure control means 33 for opening and closing the air supply passage 32.

  The extraction passage 31 returns the refrigerant gas in the crank chamber 5 to the suction chamber 7 in accordance with the refrigerant gas pressure in the crank chamber 5. The air supply passage 32 is opened and closed by the pressure control means 33 to control the amount of refrigerant gas flowing from the discharge chamber 8 toward the crank chamber 5 to adjust the pressure in the crank chamber 5, and to adjust the inclination angle of the swash plate 26. By changing the piston stroke, the discharge capacity of the compressor is changed.

  Here, the bleed passage 31 is communicated with the hollow passage (radial passage) 38s of the fixing pin 39, one end of which is exposed to the crank chamber 5, and the radial passage 38, and substantially along the axial direction in the drive shaft 10. An axial passage 10s provided, a shaft support hole 19 communicating with the axial passage 10s, an extraction groove 2s communicating with the shaft support hole 19 and provided on the rear end surface of the cylinder block 2, and the extraction groove 2 s and a bleed hole 9 s provided in the valve plate 9, and a bleed hole 6 s provided in the rear housing 6 and in communication with the bleed hole 9 s and the suction chamber 7 (FIG. 3). reference). Note that the bleed groove 2s in this case constitutes a throttle portion (orifice) that squeezes the cross-sectional area of the bleed passage 31 in the middle of the bleed passage 31. In this embodiment, the radial passage 38 s constituting the “inlet portion” of the extraction passage 31 is formed by a hollow passage of the fixing pin 38, and the protruding amount d by which the fixing pin 38 protrudes from the drive plate 21, Compared to the case where the radial passage is simply formed in the drive plate 21, the radial passage is extended.

  In this embodiment, in order to reduce the weight of the compressor 1, a dry plate 21 made of an aluminum material as a lightweight member is used. The drive plate 21 is press-fitted and fixed to the drive shaft 10 made of a steel material that requires strength and rigidity. However, since the drive plate 21 is securely fixed to the drive shaft 10 by the fixing pins 38, the inside of the compressor 1 is a medium to be compressed. Even if the press-fitting allowance is loosened due to the high temperature caused by the compression heat and the difference in thermal expansion coefficient between the drive plate 21 and the drive shaft 10, the fixed state is reliably maintained.

  The effects of this embodiment will be summarized below.

  According to the present embodiment, the drive plate 21 is integrally fixed and held with respect to the drive shaft 10 by the fixing pin 38, so that the drive plate for the drive shaft 10 can be used even if a lightweight member is used for the drive plate 21. The 21 fixed state can be reliably maintained. That is, when a light weight member is used for the drive plate 21 in order to reduce the weight of the compressor 1, there is a difference between the drive plate 21 and the drive shaft 10 due to a difference in thermal expansion coefficient between the drive plate 21 and the drive shaft 10. Although it is assumed that the press-fit is loosened due to the change, the fixed state of the drive plate 21 and the drive shaft 10 can be reliably maintained by the fixing pin 38. Thus, the weight of the compressor 1 can be reduced by using a lightweight member for the drive plate 21.

  Further, in the present embodiment, the fixing pin 38 is made of a hollow member having openings at both ends, and one end opening of the fixing pin 38 is exposed to the crank chamber 5 and the other end opening communicates with the axial passage 10s. Accordingly, the hollow passage 38s of the fixing pin 38 extending in the radial direction becomes the “inlet portion of the extraction passage 31”. For this reason, first, the mist-like oil that tries to flow into the extraction passage 31 together with the refrigerant gas from the crank chamber 5 is generated in the radial passage 38s as the “inlet portion of the extraction passage 31” as the drive shaft 10 rotates. It collides with the inner surface and is captured. Next, the oil separated from the gas in the radial passage 38 s is pushed back to the crank chamber 5 by the centrifugal force generated by the rotational movement of the drive shaft 10. Therefore, although the extraction passage 31 is a passage that always communicates the crank chamber 5 and the suction chamber 7, oil separation (gas-liquid) is actively performed at the inlet portion 38 s of the extraction passage 31 by using the rotational movement of the drive shaft 10. It becomes a structure to separate. As a result, the oil outflow from the crank chamber can be reduced with a simple configuration. In addition, oil can be constantly supplied to the sliding parts in the crank chamber 5 by the oil scattered in the crank chamber 5 from the inlet end of the radial passage 38s.

  Further, according to the present embodiment, since the distance d of the radial passage 38s of the extraction passage 31 is increased by the protrusion amount d by which the fixing pin 38 protrudes from the drive plate 21, the centrifugal separation action is further increased.

  In the present invention, a plurality of radial passages 38s may be provided along the axial direction X of the drive shaft 10, or a plurality of radial passages 38s may be provided in the circumferential direction of the drive shaft 10. Good. As described above, in the case of being configured by a plurality of radial passages, the amount of refrigerant gas flowing into one radial passage is reduced, so that the flow rate of the refrigerant gas decreases in each radial passage and the influence of the gas flow. Since it is difficult to receive the oil to which the oil is attached, there is an advantage that the centrifugal separation action can be exhibited more effectively.

  Further, the axial passage 10s may be decentered from the axis of the drive shaft 10 if the centrifugal separation action is exerted, and the radial passage 38s may be inclined with respect to the axial passage 10s.

  Furthermore, in the above-described embodiment, the swash type variable capacity compressor is shown. However, the present invention can be applied to other variable capacity compressors such as a wobble type, and of course, the fixed capacity is not limited to the variable capacity compressor. It can be applied to a compressor of the type.

It is sectional drawing of the compressor of one Embodiment of this invention. FIG. 3 is a partial cross-sectional view illustrating an action of oil separation by an inlet portion of the extraction passage in an enlarged manner on an inlet side of the extraction passage in the compressor of FIG. 1. FIG. 3 is a partial cross-sectional view illustrating an action of oil separation by an inlet portion of the extraction passage in an enlarged manner on an inlet side of the extraction passage in the compressor of FIG. 1. It is sectional drawing which expands and shows the exit side of the extraction passage in the compressor of FIG.

Explanation of symbols

1 Compressor 2 Cylinder block (housing)
3 Cylinder bore 4 Front housing (housing)
5 Crank chamber 6 Rear housing (housing)
7 Suction chamber 8 Discharge chamber 10 Drive shaft 10s Axial passage (passage)
21 Drive plate (rotating member)
29 Piston 31 Extraction passage 38 Fixing pin (Non-rotating member)
38s radial passage (extraction passage entrance)

Claims (3)

A housing (1) having a crank chamber (5), a suction chamber (7), a discharge chamber (8) and a cylinder bore (3) therein;
A drive shaft (10) rotatably supported in the crank chamber (5) and rotatably supported by the housing (4);
A rotating member (21) press-fitted into the drive shaft (10);
A piston (29) that reciprocates in the cylinder bore (3) using the rotation of the rotating member (21), and sucks, compresses, and discharges the medium to be compressed by the reciprocating motion;
An anti-rotation member (38) integrally fixing and holding the rotating member (21) with respect to the drive shaft (10);
A compressor comprising: The compressor according to claim 1,
A passage (10s) communicating with the suction chamber (7) is provided in the drive shaft (10),
The rotation preventing member (38) is formed of a hollow member having both end openings, one end opening is exposed to the crank chamber (5), and the other end opening communicates with the passage (10s). The compressor according to claim 1 or 2, wherein
The rotating member (21) is connected to a swash plate (26) for reciprocating the piston (29) and rotates integrally with the drive shaft (10) to swing the swash plate (26). A compressor characterized by being a drive plate.

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