JP2008202527A - Scroll fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll fluid machine in which an edge load acting on a main bearing is relieved (reduced) and the service life of the main bearing is prolonged (extended). <P>SOLUTION: In this scroll fluid machine 10, a small diameter shaft part 14a formed at one end of a rotating shaft 14 is pivoted by a sub bearing 16, and a large diameter shaft part 14b formed at the other end of the rotating shaft 14 is pivoted by a main bearing 15. A rotatable cylindrical ring 32 is installed between the large diameter shaft part 14b and the main bearing 15. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a scroll type fluid machine used as a compressor or an expander.

As a scroll type fluid machine used as a compressor or an expander, for example, the one disclosed in Patent Document 1 is known.
JP 2005-307948 A

  However, in the scroll type fluid machine disclosed in Patent Document 1, when the rotating shaft (crankshaft) bends or tilts, the needle bearing (main bearing) has a large edge load (at one location of the needle bearing). There is a problem that the life of the needle bearing is reduced due to the action of concentrated loads.

  The present invention has been made in view of the above circumstances, and can reduce (reduce) the edge load acting on the main bearing and can increase the life (extension) of the main bearing. An object is to provide a fluid machine.

In order to solve the above problems, the present invention employs the following means.
In the scroll type fluid machine according to the present invention, a small-diameter shaft portion formed on one end side of the rotating shaft is supported by a sub-bearing, and a large-diameter shaft portion formed on the other end side of the rotating shaft is a main bearing. The scroll type fluid machine is supported by the bearing, and a rotatable cylindrical ring is provided between the large-diameter shaft portion and the main bearing.

According to the scroll type fluid machine of the present invention, the inclination of the rotating shaft is absorbed by the slight gap formed between the outer peripheral surface of the large-diameter shaft portion of the rotating shaft and the inner peripheral surface of the cylindrical ring. As a result, the edge load acting on the main bearing (the load concentrated on one part of the main bearing) can be relaxed (reduced), and the life of the main bearing can be prolonged (extended).
Also, even if the edge load acting on the main bearing is always concentrated in one place (same place), the cylindrical ring rotates and the contact between the outer peripheral surface of the cylindrical ring and the inner peripheral surface of the main bearing changes. Concentrated fatigue generated in the main bearing can be reduced (reduced), and the life of the main bearing can be extended (extended).

  In the scroll type fluid machine, the cylindrical ring is housed in a step portion formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion, and the opening located on the open end side of the step portion. More preferably, one end surface of the cylindrical ring is restrained by a retaining plate.

According to such a scroll type fluid machine, the cylindrical ring can be easily inserted from the open end side of the stepped portion, so that the efficiency of the assembly work can be improved and the work time required for the assembly work can be shortened. Can do.
In addition, simply removing the retaining plate from the large-diameter shaft portion of the rotating shaft makes it easy to attach and detach the cylindrical ring via the open end of the stepped portion. The working time required for the work can be shortened.
Furthermore, one end surface side of the cylindrical ring is reliably restrained by the end surface (wall surface) of the stepped portion, and the other end surface side of the cylindrical ring is reliably restrained by the end surface (wall surface) of the retaining plate. Can be reliably prevented from slipping out of the stepped portion, and reliability can be ensured.

  In the scroll type fluid machine, the cylindrical ring is housed in a step portion formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion, and the opening located on the open end side of the step portion. More preferably, one end surface of the cylindrical ring is constrained by one end surface of a balance bush attached to the rotating shaft.

According to such a scroll type fluid machine, the cylindrical ring can be easily inserted from the open end side of the stepped portion, so that the efficiency of the assembly work can be improved and the work time required for the assembly work can be shortened. Can do.
In addition, simply removing the balance bush from the eccentric pin makes it possible to easily attach and detach the cylindrical ring via the open end of the stepped portion. Shortening can be achieved.
Furthermore, the other end surface side of the cylindrical ring is securely restrained by the end surface (wall surface) of the stepped portion, and the one end surface side of the cylindrical ring is reliably restrained by the end surface (wall surface) of the balance bush. It is possible to reliably prevent the stepped portion from slipping out and to ensure reliability.

  In the scroll type fluid machine, the cylindrical ring is housed in a step portion formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion, and the opening located on the open end side of the step portion. More preferably, one end surface of the cylindrical ring is constrained by the inner surface of the front housing that houses the rotating shaft.

According to such a scroll type fluid machine, the cylindrical ring can be easily inserted from the open end side of the stepped portion, so that the efficiency of the assembly work can be improved and the work time required for the assembly work can be shortened. Can do.
In addition, simply removing the front housing from the rear housing allows the cylindrical ring to be easily attached / detached via the open end of the stepped portion. Shortening can be achieved.
Furthermore, the one end surface side of the cylindrical ring is securely restrained by the end surface (wall surface) of the stepped portion, and the other end surface side of the cylindrical ring is reliably restrained by the inner surface of the front housing. It is possible to reliably prevent the slipping out and to ensure reliability.

  ADVANTAGE OF THE INVENTION According to this invention, the edge load which acts on a main bearing can be eased (reduced), and there exists an effect that the lifetime of a main bearing can be prolonged (extension).

  A first embodiment of a scroll type fluid machine (hereinafter referred to as “scroll type compressor”) according to the present invention will be described below with reference to FIG. FIG. 1 is a longitudinal sectional view of a scroll compressor according to this embodiment.

  As shown in FIG. 1, the scroll compressor 10 according to the present embodiment includes a front housing 11 and a rear housing 12, and the front housing 11 and the rear housing 12 are integrally tightened with bolts (not shown). A fixed housing 13 is provided.

  Inside the front housing 11, a crankshaft (rotating shaft) 14 is rotatably supported around a rotation axis L via a main bearing (needle bearing) 15 and a sub-bearing (needle bearing) 16. One end side (the left side in FIG. 1) of the crankshaft 14 is a small diameter shaft portion 14a, and the small diameter shaft portion 14a penetrates the front housing 11 and protrudes to one end side. An electromagnetic clutch M is mounted on the protruding portion of the small-diameter shaft portion 14a, and between the pulley 18 provided rotatably on the outer peripheral surface of the small-diameter boss portion 11a on one end side of the front housing 11 via a bearing 17. The power is intermittent. Power is transmitted to the pulley 18 from an external drive source such as an engine (not shown) via a V-belt or the like. Note that a mechanical seal (lip seal) 19 is provided between the main bearing 15 and the sub-bearing 16, thereby hermetically sealing the inside of the housing 13 and the atmosphere.

  On the other hand, a large-diameter shaft portion 14 b is provided on the other end side (right side in FIG. 1) of the crankshaft 14, and the large-diameter shaft portion 14 b has a predetermined dimension from the rotation axis L of the crankshaft 14. An eccentric pin 14c is integrally provided in an eccentric state. The large-diameter shaft portion 14b and the small-diameter shaft portion 14a of the crankshaft 14 are rotatably supported by the front housing 11 via the main bearing 15 and the sub-bearing 16, respectively. Further, the orbiting scroll member 22 is connected to the eccentric pin 14c via the balance bush 20 and the drive bearing 21, and the orbiting scroll member 22 is driven to rotate by rotating the crankshaft 14. It has become.

  The balance bush 20 is formed with a balance weight 20a for removing an unbalanced load generated when the orbiting scroll member 22 is orbitally driven. The balance weight 20a is orbited when the orbiting scroll member 22 is orbitally driven. Yes.

Inside the housing 13, a pair of fixed scroll portions 24 and a turning scroll member 22 constituting a scroll compression mechanism 23 are incorporated.
The fixed scroll member 24 includes a fixed end plate 24a and a spiral wrap 24b erected from the fixed end plate 24a. On the other hand, the orbiting scroll member 22 includes the orbiting end plate 22a and the orbiting end plate. And a spiral wrap 22b erected from 22a.

  The fixed scroll member 24 and the orbiting scroll member 22 are respectively provided with step portions (not shown) at predetermined positions along the spiral direction of the tip surfaces and bottom surfaces of the spiral wraps 24b and 22b. Then, with this stepped portion as a boundary, the outer peripheral side is higher and the inner peripheral side is lower at the tip surfaces of the spiral wraps 24b and 22b, and the outer peripheral side is lower and the inner peripheral side is higher at the bottom surface. Yes. Thereby, as for spiral wrap 24b, 22b, the lap height in the outer peripheral side is higher than the lap height in an inner peripheral side.

  As shown in FIG. 1, the fixed scroll member 24 and the orbiting scroll member 22 are incorporated in a state where the centers of the fixed scroll member 24 and the orbiting scroll member 22 are separated from each other by the orbiting radius and the spiral wraps 24b and 22b are engaged with each other with a phase difference of 180 degrees. . Thereby, a pair of compression chambers C defined by the end plates 24a and 22a and the spiral wraps 24b and 22b are formed symmetrically between the scroll members 24 and 22 with respect to the center of the scroll. Will be. In the compression chamber C, the height along the rotation axis L is higher than the height on the inner peripheral side on the outer peripheral side of the spiral wraps 24b and 22b, and the three-dimensional compression that can compress in the circumferential direction and the wrap height direction is performed. A possible compression mechanism is constructed.

The fixed scroll member 24 is fixed to the inner surface (bottom surface) of the rear housing 12 via a bolt 25. In the orbiting scroll member 22, an eccentric pin 14 c provided on one end side of the crankshaft 14 is fitted into a boss portion 26 provided on the rear surface of the orbiting end plate 22 a via a balance bush 20 and a drive bearing 21. Thus, the crankshaft 14 is connected.
Further, the orbiting scroll member 22 has a thrust receiving surface 11b formed on the front housing 11 supported on the back surface of the orbiting end plate 22a, and the orbiting scroll member 22 is interposed between the thrust receiving surface 11b and the orbiting scroll member 22 on the back surface. The orbiting scroll member 22 is configured to be revolved and driven with respect to the fixed scroll member 24 while being prevented from rotating by the rotation-preventing pinning mechanism 27 mounted.

This rotation-preventing pin ring mechanism 27 includes a pin 27a and a ring 27b, and a pin hole 11c for standing the pin 27a on one of the back surface of the fixed end plate 22a of the orbiting scroll member 22 and the thrust receiving surface 11b is provided on the other side. Is provided with a ring hole 22c for fitting the ring 27b. In the present embodiment, the thrust receiving surface 11 b is provided with a pin hole 11 c for standing the pin 27 a, and the orbiting scroll member 22 is provided with a ring hole 22 c for fitting the ring 27 b.
The pin holes 11c and the ring holes 22c are provided at a plurality of locations in the circumferential direction, generally 3 to 4 locations (4 locations in the present embodiment).

  Further, a discharge port 24c for discharging compressed refrigerant gas is opened at the center of the fixed end plate 24a of the fixed scroll member 24. The discharge port 24c is connected to the fixed end plate 24a via a retainer 28. A discharge reed valve (not shown) is provided. Further, a seal member (not shown) such as an O-ring is installed on the back surface of the fixed end plate 24 a of the fixed scroll member 24 so as to be in close contact with the inner surface of the rear housing 12. A discharge chamber 29 partitioned from the internal space (sealed space) is formed. Thereby, the internal space of the housing 13 excluding the discharge chamber 29 functions as the suction chamber 30.

Refrigerant gas returning from the refrigeration cycle is sucked into the suction chamber 30 via a suction port (not shown) provided in the front housing 11, and the fixed scroll member 24 and the orbiting scroll member are passed through the suction chamber 30. The refrigerant gas is sucked into the compression chamber C formed between the two.
A sealing member 31 such as an O-ring is installed on the joint surface between the front housing 11 and the rear housing 12, and the suction chamber 30 in the housing 13 is hermetically sealed from the atmosphere.

The scroll compressor 10 configured as described above operates as follows.
The rotational driving force transmitted from the external drive source to the pulley 18 is transmitted to the crankshaft 14 via the electromagnetic clutch M, and the crankshaft 14 is rotated. Then, the orbiting scroll member 22 connected to the eccentric pin 14c of the crankshaft 14 via the balance bush 20 and the drive bearing 21 is prevented from rotating by the rotation preventing pin ring mechanism 27 while being rotated against the fixed scroll member 24. Revolved and driven.

  The revolving orbiting drive of the orbiting scroll member 22 causes the refrigerant gas in the suction chamber 30 to be sucked into the compression chamber C formed at the outermost side in the radial direction. The compression chamber C is moved to the center side while the volume is reduced in the circumferential direction and the lap height direction after the suction is closed at a predetermined turning angle position. During this time, the refrigerant gas is compressed, and when the compression chamber C reaches a position where it communicates with the discharge port 24c, the discharge reed valve is pushed open and the compressed gas is discharged into the discharge chamber 29. It is discharged out of the compressor through a discharge port (not shown) provided in the rear housing 12.

  As shown in FIG. 1, in the present embodiment, a recess 31 is formed along the circumferential direction in the outer peripheral portion (peripheral portion) of the large-diameter shaft portion 14b of the crankshaft 14, and this A rotatable floating bush (cylindrical ring) 32 is disposed in the recess 31. The inner peripheral surface (radially inner surface) of the floating bush 32 is slightly separated from the outer peripheral surface (radially outer surface) of the large-diameter shaft portion 14b of the crankshaft 14 in the circumferential direction. The outer peripheral surface (radially outer surface) is in contact with the inner peripheral surface (radial inner side) of the main bearing 15. That is, the floating bush 32 is rotatable with respect to both the large diameter shaft portion 14 b of the crankshaft 14 and the main bearing 15.

According to the scroll compressor 10 according to the present embodiment, the crankshaft 14 has a small gap formed between the outer peripheral surface of the large-diameter shaft portion 14 b of the crankshaft 14 and the inner peripheral surface of the floating bush 32. Since the inclination is absorbed, the edge load acting on the main bearing 15 (load concentrated on one place of the main bearing 15) can be relaxed (reduced), and the life of the main bearing 15 can be extended (extended). ).
Further, even if the edge load acting on the main bearing 15 is always concentrated in one place (the same place), the floating bush 32 rotates and hits the outer peripheral surface of the floating bush 32 and the inner peripheral surface of the main bearing 15. Therefore, the intensive fatigue generated in the main bearing 15 can be reduced (reduced), and the life of the main bearing 15 can be extended (extended).

A second embodiment of the scroll compressor according to the present invention will be described with reference to FIG. FIG. 2 is an enlarged view of a main part of the scroll compressor according to the present embodiment.
In the scroll compressor according to the present embodiment, the floating bush 32 is housed in a step portion 41 formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion 14 b of the crankshaft 14. It differs from that of the first embodiment described above. Since other components are the same as those of the first embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment mentioned above.

  As shown in FIG. 2, in the present embodiment, the floating bush 32 is housed in a step portion 41 formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion 14 b of the crankshaft 14. A release plate (for example, a snap ring) 42 is provided on the open end side of the step portion 41 (on the small diameter shaft portion 14a side: the left side in FIG. 2). 32 is prevented from slipping out to the open end side of the stepped portion 41.

According to the scroll compressor according to the present embodiment, the floating bush 32 can be easily inserted from the open end side of the stepped portion 41, so that the assembly work is made efficient and the work time required for the assembly work is shortened. Can be achieved.
Further, the floating bush 32 can be easily attached and detached through the open end of the stepped portion 41 simply by removing the retaining plate 42 from the large-diameter shaft portion 14b of the crankshaft 14. It is possible to improve the efficiency and shorten the work time required for the replacement work.
Furthermore, one end surface side of the floating bush 32 is reliably restrained by the end surface (wall surface) of the step portion 41, and the other end surface side of the floating bush 32 is reliably restrained by the end surface (wall surface) of the retaining plate 42. Therefore, it is possible to reliably prevent the floating bush 32 from coming out of the stepped portion 41, and to ensure reliability.
Other functions and effects are the same as those of the above-described first embodiment, and thus description thereof is omitted here.

A third embodiment of the scroll compressor according to the present invention will be described with reference to FIG. FIG. 3 is an enlarged view of a main part of the scroll compressor according to the present embodiment.
In the scroll compressor according to the present embodiment, the floating bush 32 is housed in a step portion 51 formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion 14b of the crankshaft 14. It differs from that of the first embodiment described above. Since other components are the same as those of the first embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment mentioned above.

  As shown in FIG. 3, in this embodiment, the floating bush 32 is housed in a stepped portion 51 formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion 14 b of the crankshaft 14. One end surface of the balance bush 20 (the surface facing the end surface of the large-diameter shaft portion 14b of the crankshaft 14: the left end surface in FIG. 3) is one end surface of the floating bush 32 (the end surface on the scroll compression mechanism 23 side: FIG. 3 (protruding), which prevents the floating bush 32 from slipping out of the open end of the stepped portion 51.

According to the scroll compressor according to the present embodiment, since the floating bush 32 can be easily inserted from the open end side of the stepped portion 51, the efficiency of the assembling work is improved and the working time required for the assembling work is shortened. Can be achieved.
Further, since the floating bush 32 can be easily attached and detached through the open end of the stepped portion 51 simply by removing the balance bush 20 from the eccentric pin 14c, the replacement work of the floating bush 32 can be made more efficient. It is possible to shorten the work time required for the operation.
Furthermore, the other end surface side of the floating bush 32 is reliably restrained by the end surface (wall surface) of the step portion 51, and the one end surface side of the floating bush 32 is reliably restrained by the end surface (wall surface) of the balance bush 20. The floating bush 32 can be reliably prevented from coming out of the step portion 51, and the reliability can be ensured.
Other functions and effects are the same as those of the above-described first embodiment, and thus description thereof is omitted here.

A fourth embodiment of the scroll compressor according to the present invention will be described with reference to FIG. FIG. 4 is an enlarged view of a main part of the scroll compressor according to the present embodiment.
The scroll compressor according to this embodiment is different from that of the second embodiment described above in that the other end surface of the floating bush 32 is restrained by the inner surface (bottom surface) of the front housing 11. Since other components are the same as those of the second embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 2nd Embodiment mentioned above.

  As shown in FIG. 4, in the present embodiment, the floating bush 32 is housed in a step portion 41 formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion 14 b of the crankshaft 14. The inner surface of the front housing 11 extends (protrudes) toward the other end surface of the floating bush 32 (the end surface on the large diameter shaft portion 14b side of the crankshaft 14: the left end surface in FIG. 4). This prevents the floating bush 32 from coming out of the open end of the step portion 41.

According to the scroll compressor according to the present embodiment, the floating bush 32 can be easily inserted from the open end side of the stepped portion 41, so that the assembly work is made efficient and the work time required for the assembly work is shortened. Can be achieved.
Further, since the floating bush 32 can be easily attached and detached through the open end of the step portion 41 simply by removing the front housing 11 from the rear housing 12, the replacement work of the floating bush 32 can be made more efficient. It is possible to shorten the work time required for the operation.
Furthermore, one end surface side of the floating bush 32 is reliably restrained by the end surface (wall surface) of the step portion 41, and the other end surface side of the floating bush 32 is surely restrained by the inner surface of the front housing 11. It is possible to reliably prevent the 32 from slipping out of the stepped portion 41 and to ensure reliability.
Other functions and effects are the same as those of the above-described first embodiment, and thus description thereof is omitted here.

It is a longitudinal section of the scroll type compressor concerning a 1st embodiment of the present invention. It is a principal part enlarged view of the scroll compressor which concerns on 2nd Embodiment of this invention. It is a principal part enlarged view of the scroll compressor which concerns on 3rd Embodiment of this invention. It is a principal part enlarged view of the scroll compressor which concerns on 4th Embodiment of this invention.

Explanation of symbols

10 Scroll type compressor (scroll type fluid machine)
11 Front housing 14 Crankshaft (rotary shaft)
14a Small diameter shaft portion 14b Large diameter shaft portion 15 Main bearing 16 Sub bearing 20 Balance bush 32 Floating bush (cylindrical ring)
41 Step portion 42 Retaining plate 51 Step portion

Claims (4)

A scroll type fluid machine in which a small-diameter shaft portion formed on one end side of a rotary shaft is supported by a bearing on a sub-bearing, and a large-diameter shaft portion formed on the other end side of the rotary shaft is supported on a bearing by a main bearing. There,
A scroll type fluid machine, wherein a rotatable cylindrical ring is provided between the large-diameter shaft portion and the main bearing.   The cylindrical ring is housed in a step portion formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion, and one end surface of the cylindrical ring located on the open end side of the step portion is The scroll type fluid machine according to claim 1, wherein the scroll type fluid machine is restrained by a retaining plate.   The cylindrical ring is housed in a step portion formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion, and one end surface of the cylindrical ring located on the open end side of the step portion is The scroll fluid machine according to claim 1, wherein the scroll fluid machine is constrained by one end face of a balance bush attached to the rotating shaft.   The cylindrical ring is housed in a step portion formed along the circumferential direction on the outer peripheral portion of the large-diameter shaft portion, and one end surface of the cylindrical ring located on the open end side of the step portion is The scroll fluid machine according to claim 1, wherein the scroll fluid machine is constrained by an inner surface of a front housing that houses the rotating shaft.

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