JP2018162773A - Scroll type fluid machine and method for fixing sliding bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain deformation of a sliding bearing fixed to a boss of a turning scroll.SOLUTION: A scroll type fluid machine includes a fixed scroll and a turning scroll 340 meshed with each other, a driving force transmitting mechanism for transmitting driving force to the turning scroll 340, and a sliding bearing disposed between the driving force transmitting mechanism and an annular boss 342A formed on a back surface of the turning scroll 340. The sliding bearing is fixed in a state that a claw 342A2 positioned between a plurality of cutouts 342A1 formed on an opening end of the boss 342A of the turning scroll 340 is bent inward in a radius direction or is pushed open.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a scroll type fluid machine that compresses or expands a fluid, and a method of fixing a slide bearing to an annular boss formed on the back of a orbiting scroll.

  As an example of a scroll type fluid machine, as described in Japanese Patent Application Laid-Open No. 2002-206491 (Patent Document 1), a scroll type compressor having a fixed scroll and a turning scroll engaged with each other is known. In the scroll compressor, the orbiting scroll revolves around the axis of the fixed scroll to change the volume of the compression chamber defined by the fixed scroll and the orbiting scroll, and compresses and discharges the gas refrigerant.

  The orbiting scroll is fixed by a drive force transmission mechanism including a drive shaft, a crank pin standing upright in an eccentric state with respect to the drive shaft, and an eccentric bush fixed in an eccentric state relative to the crank pin. Revolved around the scroll axis. Here, a rolling bearing such as a roller bearing is disposed between the eccentric bush and the orbiting scroll, and relative rotation between the eccentric bush and the orbiting scroll is possible.

JP 2002-206491 A

  By the way, in the scroll compressor, for example, for the purpose of improving high speed performance, impact resistance, and quietness, it has been studied to use a sliding bearing instead of a rolling bearing. In this case, after the sliding bearing is press-fitted into the annular boss formed on the back surface of the orbiting scroll, the opening end of the boss is plastically deformed radially inward to fix the sliding bearing to the boss. Conceivable. However, if the opening end of the boss part is plastically deformed radially inward, the inner peripheral surface of the opening end of the boss part causes deformation at one end of the slide bearing, for example, the clearance in the radial direction with the fitting part is appropriate. It will not be kept at this level, and the quality will be affected. In addition, if the rolling bearing is press-fitted into the boss part of the orbiting scroll and then the opening end of the boss part is plastically deformed radially inward, the outer ring of the rolling bearing will be deformed, but this will affect the roller. It did not reach.

  Accordingly, an object of the present invention is to provide a scroll type fluid machine and a sliding bearing fixing method in which deformation of the sliding bearing is suppressed by reviewing a structure for fixing the sliding bearing to the boss portion of the orbiting scroll. To do.

  For this reason, the scroll type fluid machine includes a fixed scroll and an orbiting scroll that are meshed with each other, a driving force transmission mechanism that transmits a driving force to the orbiting scroll, and an annular ring formed on the back surface of the driving force transmission mechanism and the orbiting scroll. And a sliding bearing disposed between the boss portion having a shape. And a slide bearing is fixed in the state which the nail | claw part located between the some notch parts formed in the opening end of the boss | hub part of a turning scroll was bent in the radial inward state, or was expanded.

  Further, in the sliding bearing fixing method, the sliding bearing is press-fitted into an annular boss formed on the back surface of the orbiting scroll, and a plurality of notches formed at the opening end of the orbiting scroll boss is formed. Bend or push out the nail part that is located inward, and fix the sliding bearing on one side of the nail part.

  ADVANTAGE OF THE INVENTION According to this invention, in a scroll type fluid machine, a deformation | transformation of the slide bearing fixed with respect to the boss | hub part of a turning scroll can be suppressed.

It is sectional drawing which shows an example of a scroll type compressor. It is a perspective view which shows an example of the fixation structure of a slide bearing. It is a side view which shows an example of the fixation structure of a slide bearing. It is explanatory drawing of the method of fixing a slide bearing to the boss | hub part of a turning scroll. It is a principal part expanded sectional view which shows the 1st device which reduces the influence on a slide bearing. It is a principal part expanded sectional view which shows the device which bends the nail | claw part of a turning scroll. It is a principal part expanded sectional view which shows the 2nd device which reduces the influence on a slide bearing. It is a principal part expanded sectional view which shows the 3rd device which reduces the influence on a slide bearing. It is a top view which shows 1st Example of a rotation prevention mechanism. It is a principal part expanded sectional view which shows 1st Example of a rotation prevention mechanism. It is a top view which shows 2nd Example of a rotation prevention mechanism. It is a principal part expanded sectional view which shows 2nd Example of a rotation prevention mechanism.

Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the accompanying drawings.
As the scroll type fluid machine, either a compressor or an expander can be used. Here, a scroll type compressor will be described as an example.

FIG. 1 shows an example of a scroll compressor.
The scroll compressor 100 is incorporated in a refrigerant circuit of a vehicle air conditioner, for example, and compresses and discharges a gaseous refrigerant (fluid) sucked from the low pressure side of the refrigerant circuit. The scroll compressor 100 includes a housing 200, a compression mechanism 300 that compresses a low-pressure gaseous refrigerant, and a driving force transmission mechanism 400 that transmits a driving force to the compression mechanism 300 from the outside. Here, as the refrigerant, for example, HFC refrigerant R134A or the like can be used.

  The housing 200 is separable, and includes a front housing 220 that accommodates the compression mechanism 300 and the driving force transmission mechanism 400, and is joined to an opening end of the front housing 220 to form a discharge chamber H 1 for gaseous refrigerant compressed by the compression mechanism 300. And a rear housing 240.

  The outer peripheral surface of the front housing 220 is formed in a stepped columnar shape whose outer diameter is reduced in four steps as the distance from the joint surface with the rear housing 240 increases. Here, the columnar shape may be a level that can be recognized as a columnar shape by appearance, and may include, for example, reinforcing ribs, mounting bosses, and the like on the outer peripheral surface (the same applies to the following). In addition, the inner peripheral surface of the front housing 220 is formed in a stepped columnar shape whose outer diameter is reduced in four steps as the distance from the joint surface with the rear housing 240 increases. Accordingly, the front housing 220 has a similar shape between the outer peripheral surface and the inner peripheral surface, and has a substantially identical outer shell thickness, and is formed in a cylindrical shape that is reduced in diameter in four stages. Furthermore, a suction port (not shown) that sucks gaseous refrigerant from the low pressure side of the refrigerant circuit to the outer periphery of the compression mechanism 300 is formed on the peripheral wall of the front housing 220.

  In the following description, for convenience of description, the first inner peripheral surface 220A, the second inner peripheral surface 220B, and the third inner surface of the stepped columnar inner peripheral surface of the front housing 220 from the large diameter portion to the small diameter portion. The peripheral surface 220C and the fourth inner peripheral surface 220D are referred to.

  The rear housing 240 has a hemispherical shape in which the center portion bulges outward as the distance from the joint surface with the front housing 220 increases. Therefore, the rear housing 240 forms an internal space having a predetermined volume, which functions as the discharge chamber H1. Further, a discharge port (not shown) for discharging the compressed refrigerant from the discharge chamber H1 to the high pressure side of the refrigerant circuit is formed on the peripheral wall of the rear housing 240.

  The front housing 220 and the rear housing 240 are separable via a plurality of bolts 500 serving as fasteners, for example, in a state in which the opening end of the large-diameter side of the front housing 220 and the opening end of the rear housing 240 are joined. It is concluded. For this reason, boss portions 222 that extend along the axial direction from the large diameter portion toward the small diameter portion and are engaged with the shaft portion of the bolt 500 are formed at a plurality of spaced positions on the outer peripheral surface of the front housing 220. Has been. On the other hand, bolts extending along the axial direction from the opening end to the bulging direction at a plurality of spaced positions on the outer peripheral surface of the rear housing 240 and corresponding to the boss portion 222 of the front housing 220. Boss portions 242 through which 500 shaft portions pass are formed. Accordingly, with the front housing 220 and the rear housing 240 joined, the shaft portion of the bolt 500 is inserted from the outside of the rear housing 240 into the boss portion 242, and the shaft portion is inserted into the boss portion 222 of the front housing 220. By screwing, the housing 200 in which the front housing 220 and the rear housing 240 are integrated is configured.

  The compression mechanism 300 is disposed in a cylindrical space defined by the first inner peripheral surface 220 </ b> A of the front housing 220. Specifically, the compression mechanism 300 includes a fixed scroll 320 disposed so as to close the large-diameter opening of the front housing 220, the fixed scroll 320, the first inner peripheral surface 220A, and the second inner peripheral surface 220B. , Orbiting scroll 340 disposed between the step portions.

  The fixed scroll 320 includes a disc-shaped bottom plate 322 fitted to the opening end of the first inner peripheral surface 220A of the front housing 220, and an involute curve wrap (spiral shape) extending from one surface of the bottom plate 322 toward the orbiting scroll 340. Blades) 324 and a thin annular ring shape extending radially outward from the outer peripheral surface of the bottom plate 322 at the opening end of the first inner peripheral surface 220A and sandwiched between the joint surfaces of the front housing 220 and the rear housing 240. And a flange 326. The outer peripheral edge of the flange 326 is formed in a shape that follows the outer shape of the opening end on the large-diameter side of the front housing 220, and through holes through which the shaft portions of the bolts 500 can pass are formed at a plurality of predetermined positions on the plate surface. Is formed. Accordingly, the fixed scroll 320 is sandwiched between the joint surfaces of the front housing 220 and the rear housing 240 via the flange 326, closes the opening on the large diameter side of the front housing 220, and cooperates with the rear housing 240. The discharge chamber H1 is partitioned.

  The orbiting scroll 340 has a disc-shaped bottom plate 342 disposed on the step side of the first inner peripheral surface 220A and the second inner peripheral surface 220B, and an involute curve extending from one surface of the bottom plate 342 toward the fixed scroll 320. And a wrap 344. The bottom plate 342 has an outer diameter smaller than that of the bottom plate 322 of the fixed scroll 320, and the other surface transmits a thrust force to the step portions of the first inner peripheral surface 220A and the second inner peripheral surface 220B. The thrust plate 510 is in contact with the stepped portion.

  Then, the fixed scroll 320 and the orbiting scroll 340 are meshed so that the side walls of the wraps 324 and 344 are partially in contact with each other with the circumferential angles of the wraps 324 and 344 being shifted from each other. At this time, a tip seal (not shown) that secures the sealing performance with the bottom plate 342 of the orbiting scroll 340 is embedded at the tip of the wrap 324 of the fixed scroll 320. On the other hand, a tip seal (not shown) that secures the sealing performance with the bottom plate 322 of the fixed scroll 320 is embedded at the tip of the wrap 344 of the orbiting scroll 340. Therefore, in the compression mechanism 300, a crescent-shaped sealed space, that is, a compression chamber H2 for compressing the gaseous refrigerant is defined between the fixed scroll 320 and the orbiting scroll 340.

  A discharge hole 322A for discharging the gaseous refrigerant compressed by the compression chamber H2 to the discharge chamber H1 is formed at the center of the bottom plate 322 of the fixed scroll 320. On the other surface of the bottom plate 322, the flow of the gaseous refrigerant from the compression chamber H2 to the discharge chamber H1 is allowed, while the flow of the gaseous refrigerant from the discharge chamber H1 to the compression chamber H2 is prevented. A directional valve 328 is attached.

  On the outer peripheral surface of the bottom plate 322 of the fixed scroll 320, a concave groove 322B is formed over its entire length, and an O-ring 322C that secures a seal with the front housing 220 is fitted. Further, a concave groove 240A is formed over the entire length of the opening end surface of the rear housing 240, and an O-ring 240B that secures a seal with the front housing 220 is fitted therein.

  The driving force transmission mechanism 400 includes a driving shaft 410, a crankpin 420, an eccentric bush 430, a balancer weight 440, an electromagnetic clutch 450, and a pulley 460.

  The drive shaft 410 has a stepped columnar shape having a small diameter portion 410A and a large diameter portion 410B, and the front housing 220 is arranged such that the tip of the small diameter portion 410A protrudes from the small diameter side end of the front housing 220 to the outside. Rotation is freely accommodated. Specifically, the small-diameter portion 410A and the large-diameter portion 410B of the drive shaft 410 have a ball bearing 520 and a roller bearing 530 with respect to the opening side end portion of the fourth inner peripheral surface 220D and the third inner peripheral surface 220C, respectively. It is pivotally supported via a shaft. A portion of the small diameter portion 410A of the drive shaft 410 located between the ball bearing 520 and the large diameter portion 410B is, for example, a fourth inner periphery of the front housing 220 by a seal member 540 such as a mechanical seal or a lip seal. The sealing property with the surface 220D is ensured.

  A cylindrical crankpin 420 that protrudes from the axial center toward the compression mechanism 300 is erected at one end face in the axial direction of the large-diameter portion 410B of the drive shaft 410. On the outer peripheral surface of the crankpin 420, an eccentric bushing 430 having a cylindrical outer shape, in which a fitting hole into which the crankpin 420 is fitted so as to be relatively rotatable, is fixed in an eccentric state. The outer peripheral surface of the eccentric bush 430 has a sliding bearing 550 that is press-fitted into the inner peripheral surface of an annular boss portion 342A that extends from the other surface (back surface) of the bottom plate 342 of the orbiting scroll 340 to the smaller diameter side of the front housing 220. It is supported through freely rotating.

  Further, one end face in the axial direction of the large-diameter portion 410B of the drive shaft 410 is directed toward the inside of the large-diameter portion 410B at an eccentric position opposite to the formation position of the crankpin 420 with respect to the axial center. An extending circular hole 410C is formed. A cylindrical pin 430A is formed on the end face of the eccentric bushing 430 facing the one end face of the large-diameter portion 410B, extending from the position eccentric to the axial center toward the large-diameter portion 410B. The pin 430A of the eccentric bush 430 is fitted so as to revolve around the axis while being inscribed in the circular hole 410C of the drive shaft 410. Accordingly, the orbiting scroll 340 revolves around the axis of the fixed scroll 320 in a state in which the rotation is prevented. Furthermore, a balancer weight 440 corresponding to the weight of the orbiting portion is attached to the outer side of the boss portion 342A of the orbiting scroll 340 in order to reduce vibration caused by the revolution orbiting motion of the orbiting scroll 340.

  The distal end portion of the drive shaft 410 is connected to a pulley 460 that is rotated by power from the outside via an electromagnetic clutch 450 that is mounted on the outer peripheral surface of the small-diameter portion of the front housing 220 so as to be free to rotate. Therefore, when the electromagnetic clutch 450 is operated, the pulley 460 and the drive shaft 410 are connected, and the drive shaft 410 is rotated by the rotational force of the pulley 460. On the other hand, when the operation of the electromagnetic clutch 450 is stopped, the connection between the pulley 460 and the drive shaft 410 is released, and the rotation of the drive shaft 410 is stopped. Thus, the operation of the scroll compressor 100 can be controlled by appropriately controlling the electromagnetic clutch 450.

Next, the operation of the scroll compressor 100 will be described.
When the drive shaft 410 is rotated by power from the outside, the rotational force is transmitted to the orbiting scroll 340 via the crank pin 420 and the eccentric bush 430, and the orbiting scroll 340 is revolved around the axis of the fixed scroll 320. As a result, the volume of the compression chamber H2 of the compression mechanism 300 changes, and the low-pressure gaseous refrigerant sucked into the internal space from the suction port of the front housing 220 is guided to the center while being compressed in the compression chamber H2. The gaseous refrigerant guided to the center of the compression mechanism 300 is discharged into the discharge chamber H1 through the discharge hole 322A and the one-way valve 328 formed in the bottom plate 322 of the fixed scroll 320. The gaseous refrigerant discharged to the discharge chamber H1 is discharged to the high pressure side of the refrigerant circuit via the discharge port of the rear housing 240.

  By the way, when the sliding bearing 550 is press-fitted and fixed to the boss portion 342A of the orbiting scroll 340, like the rolling bearing, if the opening end of the boss portion 342A is plastically deformed radially inward, the opening end of the boss portion 342A is There is a possibility that one end of the sliding bearing 550 is deformed by the deformation. If the sliding bearing 550 is deformed, for example, the radial clearance is not properly maintained, which affects the quality and the like. Therefore, the structure for fixing the sliding bearing 550 to the boss portion 342A of the orbiting scroll 340 is reviewed to prevent deformation of the sliding bearing 550.

2 and 3 show an example of a structure for fixing the slide bearing 550. FIG.
The opening end (tip portion) of the boss portion 342A of the orbiting scroll 340 has its outer peripheral surface thinned so that it can be easily bent inward by caulking (caulking). Is also formed in a thin annular shape. A plurality of cutout portions 342A1 extending from the end surface along the axial direction are formed at the opening end of the boss portion 342A at equal intervals (equal angles). In the example shown in the figure, eight notches 342A1 are formed, but it is sufficient that at least three notches 342A1 are formed. In addition, the shape of the notch 342A1 is a semicircle (a missing circle) in the illustrated example, but may be an arbitrary shape such as a rectangular shape, a triangular shape, an elliptical shape, or a trapezoidal shape. Here, in the boss portion 342A of the orbiting scroll 340, a portion located between the plurality of notch portions 342A1 formed at the opening end is a claw portion 342A2 for fixing the slide bearing 550, as will be described later. Function.

  When the sliding bearing 550 is fixed to the boss portion 342A of the orbiting scroll 340, as shown in FIG. 4, the sliding bearing 550 is press-fitted into the inner peripheral surface of the boss portion 342A from the outside of the orbiting scroll 340. Then, for example, by using a caulking tool, the claw portion 342A2 formed at the opening end of the boss portion 342A is spread radially inward from above and plastically deformed, and one surface of the claw portion 342A2, that is, the boss portion 342A One end portion (upper end portion in the figure) of the sliding bearing 550 is locked and fixed on one surface continuous with the inner peripheral surface. Here, “fixed” means that the slide bearing 550 is prevented from falling off from the boss portion 342A of the orbiting scroll 340.

  According to such a fixing structure, the sliding bearing 550 is fixed to the boss portion 342A of the orbiting scroll 340 by moving the claw portions 342A2 positioned between the plurality of cutout portions 342A1 formed at the opening ends of the boss portion 342A inwardly. It is done by spreading it out. For this reason, as compared with the technique of plastically deforming the entire circumference of the open end of the boss portion 342A radially inward, it is only necessary to plastically deform only the claw portion 342A2 inward of the radius, and the open end of the boss portion 342A. It is possible to suppress the deformation of the slide bearing 550 caused by the inner peripheral surface. Therefore, for example, the radial clearance can be properly maintained, and the influence on quality and the like can be reduced. In addition, the load required for bending by caulking can be reduced by appropriately adjusting the number, shape, circumferential length, and the like of the notch portion 342A1 formed at the opening end of the boss portion 342A, and the sliding bearing 550 It is also possible to mitigate deformations in the vicinity.

  In order to further reduce the influence of the claw portion 342A2 on the sliding bearing 550, the shape of the claw portion 342A2 or the sliding bearing 550 can be devised as exemplified below. In addition, the following devices can be used alone or in combination.

FIG. 5 shows a first device for reducing the influence on the sliding bearing 550.
In the boss portion 342A of the orbiting scroll 340, the inner peripheral surface of the claw portion 342A2 located at the opening end thereof is formed in a tapered shape whose inner diameter gradually increases toward the opening end of the boss portion 342A. The taper angle of the tapered shape may be an angle at which a minimum pressing force capable of fixing the sliding bearing 550 by the claw portion 342A2 can be applied when the claw portion 342A2 is bent inward in the radius, for example. The tapered shape is not limited to the inner peripheral surface of the claw portion 342A2, but may be formed over the entire circumference of the open end of the boss portion 342A, for example, for the purpose of facilitating the taper processing (the same applies hereinafter). ).

  According to the first device, since the inner peripheral surface of the claw portion 342A2 is formed in a tapered shape, when the claw portion 342A2 of the boss portion 342A is bent radially inward, the bending angle of the claw portion 342A2 is increased. It is suppressed. For this reason, the pressing force transmitted in the radial direction of the sliding bearing 550 from the claw portion 342A2 is reduced, and deformation of the sliding bearing 550 can be suppressed. Further, since the inner peripheral surface of the claw portion 342A2 is formed in a tapered shape, the work of press-fitting the slide bearing 550 into the inner peripheral surface of the boss portion 342A can be facilitated.

  Note that, in the boss portion 342A of the orbiting scroll 340, the outer peripheral surface of the claw portion 342A2 located at the opening end thereof has a tapered shape in which the outer diameter gradually decreases toward the opening end of the boss portion 342A as shown in FIG. It may be formed. In this case, the taper shape of the outer peripheral surface of the claw portion 342A2 can have a larger taper angle than the taper shape of the inner peripheral surface of the claw portion 342A2. In this way, the claw portion 342A2 can be bent from the direction along the axis of the boss portion 342A, and the influence on the sliding bearing 550 can be further reduced.

FIG. 7 shows a second device for reducing the influence on the sliding bearing 550.
A circumferential groove 342A3 that avoids contact with one end of the sliding bearing 550 is formed on the inner peripheral surface of the boss portion 342A of the orbiting scroll 340. The circumferential groove 342A3 has a shape and size capable of avoiding contact with a corner portion located on the outer peripheral side of one end of the sliding bearing 550 when the sliding bearing 550 is press-fitted to the boss portion 342A to a predetermined position. have.

  According to the second device, since the circumferential groove 342A3 is formed on the inner circumferential surface of the boss portion 342A, when the claw portion 342A2 of the boss portion 342A is bent radially inward, the corner portion of the sliding bearing 550 is formed. Is accommodated in the circumferential groove 342A3, and contact with the boss portion 342A is avoided. For this reason, the pressing force transmitted from the claw portion 342A2 in the radial direction of the sliding bearing 550 is reduced, and deformation of the sliding bearing 550 can be suppressed.

FIG. 8 shows a third device for reducing the influence on the sliding bearing 550.
The inner peripheral surface located at one end of the sliding bearing 550 is formed as a large-diameter portion 550A having a larger diameter than the inner peripheral surface of the other portion. Here, the large-diameter portion 550A of the sliding bearing 550 has an annular shape in the illustrated example. However, when the claw portion 342A2 of the boss portion 342A is bent inward, the influence of the sliding bearing 550 is affected. The inner peripheral surface can have any shape that does not deform radially inward from the inner peripheral surface of the other part.

  According to the third device, since the large-diameter portion 550A is formed on the inner peripheral surface of the slide bearing 550, when the claw portion 342A2 of the boss portion 342A is bent inward in the radial direction, the influence is slippery. Even if it reaches the bearing 550, the inner peripheral surface of the sliding bearing 550 does not protrude radially inward. For this reason, even if the sliding bearing 550 is slightly deformed, for example, the radial clearance can be properly maintained.

  By the way, the sliding bearing 550 fixed to the boss portion 342A of the orbiting scroll 340 only needs to be able to rotate relative to the eccentric bush 430 of the driving force transmission mechanism 400, and therefore, it prevents relative rotation with the boss portion 342A. Is desirable. For this reason, as illustrated below, the boss portion 342A or the sliding bearing 550 of the orbiting scroll 340 is provided with a rotation prevention mechanism.

9 and 10 show a first embodiment of the rotation prevention mechanism.
At one end portion of the sliding bearing 550, at least one convex portion 550B that is engaged with the notch portion 342A1 of the boss portion 342A of the orbiting scroll 340 is formed. The convex portion 550B is preferably formed, for example, at at least two positions of the axial object with respect to the central axis of the boss portion 342A so that a force that is applied to the sliding bearing 550 does not act. Further, the shape of the convex portion 550B can be a shape that follows the notch 342A1 of the boss portion 342A, but can also be an arbitrary shape that can prevent the rotation of the slide bearing 550.

  According to the first embodiment of the rotation preventing mechanism, when the sliding bearing 550 is press-fitted into the boss portion 342A of the orbiting scroll 340, the convex portion 550B formed at one end of the sliding bearing 550 is formed as shown in FIG. The boss 342A is engaged with the notch 342A1. For this reason, in a state where the claw portion 342A2 of the boss portion 342A is bent radially inward and the slide bearing 550 is fixed, the projection 550B can prevent the slide bearing 550 from rotating with respect to the boss portion 342A.

11 and 12 show a second embodiment of the rotation prevention mechanism.
At one end of the sliding bearing 550, at least one concave portion 550C that is engaged with the claw 342A2 when the claw 342A2 of the boss 342A of the orbiting scroll 340 is bent radially inward is formed. The concave portion 550C is preferably formed at least at two positions of the axial object with respect to the central axis of the sliding bearing 550, for example, so as not to exert a force acting on the sliding bearing 550.

  According to the second embodiment of the rotation preventing mechanism, when the sliding bearing 550 is press-fitted into the boss portion 342A of the orbiting scroll 340 and the claw portion 342A2 of the boss portion 342A is bent inward in the radius, as shown in FIG. The claw portion 342A2 engages with the concave portion 550C of the slide bearing 550. For this reason, when the claw part 342A2 of the boss part 342A is bent inward in the radius direction, the rotation of the sliding bearing 550 relative to the boss part 342A can be prevented and the sliding bearing 550 can be fixed to the boss part 342A.

  As mentioned above, although embodiment for implementing this invention was described, this invention is not restrict | limited to the said embodiment, As shown in an example below, various deformation | transformation and change are based on a technical idea. Is possible.

  The driving force transmission mechanism 400 only needs to include at least the driving shaft 410, the crankpin 420, and the eccentric bush 430. In addition, regarding the various technical ideas described above, on the premise that there is no technical contradiction, a part thereof can be replaced with another technical idea, or a plurality of technical ideas can be combined.

100 scroll type compressor (scroll type fluid machine)
320 Fixed scroll 340 Orbiting scroll 342A Boss part 342A1 Notch part 342A2 Claw part 342A3 Circumferential groove 400 Driving force transmission mechanism 410 Drive shaft 420 Crank pin 430 Eccentric bush 550 Slide bearing 550A Large diameter part 550B Convex part 550C Concave part

Claims (8)

Fixed and orbiting scrolls meshed with each other;
A driving force transmission mechanism for transmitting a driving force to the orbiting scroll;
A sliding bearing disposed between the driving force transmission mechanism and an annular boss formed on the back of the orbiting scroll;
A scroll type fluid machine comprising:
The sliding bearing is fixed in a state in which a claw portion located between a plurality of cutout portions formed at an opening end of a boss portion of the orbiting scroll is bent in a radially inward state or expanded.
Scroll type fluid machine. The inner peripheral surface of the claw portion is formed in a tapered shape whose inner diameter increases toward the opening end of the boss portion.
The scroll type fluid machine according to claim 1. The outer peripheral surface of the claw portion has a tapered shape in which the outer diameter decreases toward the opening end of the boss portion, and the tapered shape is formed on the inner peripheral surface located at the opening end of the boss portion of the orbiting scroll. Is also formed in a tapered shape with a large taper angle,
The scroll type fluid machine according to claim 2. On the inner circumferential surface of the boss portion of the orbiting scroll, a circumferential groove that avoids contact with one end portion of the sliding bearing is formed,
The scroll type fluid machine according to any one of claims 1 to 3. The inner peripheral surface located at one end of the sliding bearing is formed with a larger diameter than the inner peripheral surface of the other part.
The scroll type fluid machine according to any one of claims 1 to 4. At one end of the sliding bearing, at least one convex portion that is locked to a notch portion of the boss portion of the orbiting scroll is formed,
The scroll type fluid machine according to any one of claims 1 to 5. At one end portion of the sliding bearing, in a state where the claw portion is bent radially inward, at least one concave portion to be engaged with the claw portion is formed,
The scroll type fluid machine according to any one of claims 1 to 6. Press the slide bearing into the annular boss formed on the back of the orbiting scroll,
Bend or push the claw portion located between the plurality of notches formed at the opening end of the boss portion of the orbiting scroll inwardly,
Fixing the sliding bearing on one surface of the claw portion;
How to fix the slide bearing.