JP6460710B2 - Scroll type fluid machinery - Google Patents

Description

  The present invention relates to a scroll type fluid machine, and more particularly to a scroll type fluid machine used in a refrigeration circuit of a vehicle air conditioner.

There is known a scroll type fluid machine provided with a rotation prevention mechanism for preventing the rotation of the movable scroll without hindering the revolution of the movable scroll with respect to the fixed scroll fixed to the casing.
As the rotation prevention mechanism, a so-called pin-and-ring type rotation prevention mechanism having a plurality of sets of rotation prevention pins (hereinafter also simply referred to as pins) and a regulation ring (hereinafter also simply referred to as a ring) is known. .

  The pin has, for example, a protruding portion that is erected from a base portion of a casing that is positioned to face the substrate on which the spiral wall of the movable scroll is erected and protrudes toward the substrate of the movable scroll. Moreover, the ring is press-fitted into a restriction hole formed in the back surface of the substrate of the movable scroll, for example. The protruding portion of the pin is loosely fitted to the ring and is slid on the inner peripheral surface of the ring by the revolving orbiting motion of the movable scroll with respect to the fixed scroll.

And in patent document 1, even if the positional relationship of a pin and a ring changes by making the protrusion part of a pin into a taper shape, the surface contact of a pin and a ring is maintained appropriately, and the contact surface pressure of the pin with respect to a ring A fluid machine that reduces pin wear and suppresses pin wear is disclosed.
Further, in Patent Document 2, an elastic member is partially interposed between the ring and the receiving hole, so that the impact force when the projecting portion of the pin is slid on the inner peripheral surface of the ring, and hence the cause. A scroll compressor that suppresses noise is disclosed.

Japanese Patent No. 4884904 JP 2008-208715 A

The rotation of the movable scroll becomes faster, and the turning load of the movable scroll (the pressing force of the movable scroll against the fixed scroll) increases, so that the axis of the pin intersects the height direction of the ring, and the pin tilts. is there.
In Patent Document 1, by making the protruding portion of the pin into a tapered shape, the contact area between the inclined protruding portion of the pin and the inner peripheral surface of the ring is increased, and as a result, the contact surface pressure of the pin with respect to the ring can be reduced. Therefore, pin wear can be suppressed.

  However, when the rotation of the movable scroll becomes slow, the turning load of the movable scroll decreases, and the pin axis is parallel to the height direction of the ring, the tip of the protruding portion of the pin is tapered. On the contrary, the contact area between the pin and the inner peripheral surface of the ring is reduced, and the contact surface pressure of the pin with respect to the ring is increased. Therefore, when the fluid machine is used at a low load for a long time, the wear of the pin may be promoted.

  On the other hand, in Patent Document 2, when an elastic member is partially interposed between the ring and the receiving hole, the impact force can be absorbed when the protruding portion of the pin is slid on the inner peripheral surface of the ring. However, the ring is partially bent in the radial direction and elastically deformed, and the shape of the ring viewed from the height direction of the ring cannot be maintained in a perfect circle. Therefore, the noise of the compressor may increase and the wear of the pins may be partially promoted.

Furthermore, when the revolving rotation of the orbiting scroll becomes high speed and the orbiting load of the orbiting scroll increases, the axis of the pin intersects the height direction of the ring, and when the pin is inclined, the root of the protruding part of the pin is the ring. The edge of the open end may hit the edge. In Patent Documents 1 and 2, no special consideration is given to the wear of the pins caused by this edge contact.
The present invention has been made in view of such a problem, and an object of the present invention is to provide a scroll capable of improving both durability and quietness regardless of the operation state of the scroll type fluid machine. It is to provide a mold fluid machine.

In order to achieve the above object, a scroll type fluid machine according to the present invention is a scroll type equipped with a rotation prevention mechanism for preventing the rotation of the movable scroll without hindering the revolution orbiting motion of the movable scroll with respect to the fixed scroll fixed to the casing. A rotation prevention mechanism, which is a fluid machine, includes: a substrate on which a spiral wall of a movable scroll is erected; and a rotation prevention pin that is erected from any one of a pedestal portion of a casing that is positioned to face the substrate; And a restricting ring that is press-fitted into a receiving hole drilled in the other of the pedestal part and loosely fitted with the rotation prevention pin, and the protrusion of the rotation prevention pin is formed in the opening of the accommodation hole. when sliding on the inner peripheral surface, relief space to allow expansion due to elastic deformation of the restriction ring is secured, relief space, Wataru the inner peripheral surface its entire circumference at the opening of the accommodation hole The inner circumferential surface of the receiving hole is formed by press-fitting and fixing the regulating ring into the press-fitting surface, and extends from the press-fitting surface portion toward the opening end of the opening, and is inclined in the direction of expanding the receiving hole. And a counterbore surface portion extending from the taper surface portion toward the opening end and having the same diameter as the largest diameter portion of the taper surface portion, and the escape space includes an outer peripheral surface of the regulating ring, a taper surface portion and a counterbore surface portion. Formed between .

Preferably, the clearance space length in the height direction of the restriction ring in the clearance space is a maximum of 20% of the total ring length in the height direction of the restriction ring.

  According to the scroll type fluid machine of the present invention, both durability and quietness can be improved regardless of the operation state of the scroll type fluid machine.

It is a longitudinal section of a scroll compressor concerning one embodiment of the present invention. It is the top view which looked at the rotation prevention mechanism of FIG. 1 from the AA direction of FIG. FIG. 3 is an enlarged cross-sectional view of the pair of rings and the accommodation hole of FIG. 2 as seen from the BB direction of FIG. 2. It is the expanded sectional view which expanded and showed the escape space of FIG. It is sectional drawing which showed the state which the base part of the pin of FIG. 1 contacted the edge of the edge of the opening part of a ring temporarily. FIG. 6 is a cross-sectional view showing a state where the inclined pin of FIG. 5 is further pressed against the ring and the ring is expanded and deformed.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention. The compressor 1 is incorporated in, for example, a refrigeration circuit of a vehicle air conditioner mounted on a vehicle (not shown). The refrigeration circuit has a refrigerant circulation path for the refrigerant that is the working fluid of the compressor 1, and the compressor 1 sucks the refrigerant from the return path of the refrigerant circulation path, compresses the refrigerant, and discharges the refrigerant toward the forward path of the refrigerant circulation path. .

  As shown in FIG. 1, the compressor 1 includes a rear casing 2 and a front casing (casing) 4. A scroll unit 6 is disposed between the rear casing 2 and the front casing 4. A drive shaft 8 extends into the front casing 4, and the drive shaft 8 is rotatably supported by the front casing 4 via a bearing. The front casing 4 is provided with a pedestal portion 4a projecting inward.

  A drive pulley 12 incorporating an electromagnetic clutch 10 is attached to the projecting end of the drive shaft 8 from the front casing 4. The drive pulley 12 is rotatably supported by the front casing 4 via a bearing. The power of the vehicle engine is transmitted to the drive pulley 12 via a drive belt (not shown), and the rotation of the drive pulley 12 can be transmitted to the drive shaft 8 via the electromagnetic clutch 10. Therefore, when the electromagnetic clutch 10 is turned on during driving of the engine, the drive shaft 8 rotates integrally with the drive pulley 12.

  The scroll unit 6 includes a fixed scroll 14 and a movable scroll 16. The movable scroll 16 is assembled so as to mesh with the fixed scroll 14. The fixed scroll 14 is positioned between the rear casing 2 and the front casing 4 and is sandwiched between the rear casing 2 and the front casing 4 by a plurality of fixing bolts (not shown) extending in the axial direction of the drive shaft 8.

The movable scroll 16 includes a substrate 16 a, and a spiral wall 16 b is erected on the substrate 16 a toward the fixed scroll 14. The back surface 16c of the substrate 16a of the movable scroll 16 is positioned to face the pedestal 4a of the front casing.
A spiral wall 14 b is also erected on the substrate 14 a of the fixed scroll 14 toward the substrate 16 a of the movable scroll 16. Then, the spiral walls 14b and 16b of the fixed scroll 14 and the movable scroll 16 are engaged with each other to form a compression chamber 18 of refrigerant that is a working fluid of the compressor 1, and the volume of the compression chamber 18 is fixed scroll. 14 is increased or decreased as the orbiting scroll 16 revolves with respect to 14.

  The end wall 4 b of the front casing 4 is in contact with the outer peripheral portion of the spiral wall 14 b of the fixed scroll 14, and the substrate 16 a of the movable scroll 16 is positioned in the front casing 4. A refrigerant suction chamber 20 is secured between the end wall 4b of the front casing 4 and the substrate 16a. The suction chamber 20 communicates with the return path of the refrigerant circulation path described above.

  A substrate 14 a of the fixed scroll 14 is in contact with the end wall 2 a of the rear casing 2. A refrigerant discharge chamber 22 partitioned from the substrate 14 a is formed in the rear casing 2, and the discharge chamber 22 communicates with the aforementioned refrigerant circulation path. Further, the discharge chamber 22 communicates with the compression chamber 18 through a discharge hole 24 drilled in the substrate 14 a of the fixed scroll 14. A discharge valve 26 for opening and closing the discharge hole 24 is disposed in the discharge chamber 22, and the opening degree of the discharge valve 26 is regulated by a stopper plate 28.

  A boss 30 projects from the back surface 16c of the substrate 16a of the movable scroll 16, and a bush 32 is rotatably inserted into the boss 30 through a bearing. An eccentric shaft portion 8 a of the drive shaft 8 is eccentrically supported on the bush 32, and a revolving orbiting motion is imparted to the movable scroll 16 by the rotation of the drive shaft 8. Further, a ring plate-shaped thrust plate 34 is disposed between the back surface 16 c of the substrate 16 a of the movable scroll 16 and the pedestal portion 4 a of the front casing 4. When the orbiting scroll 16 revolves, the back surface 16 c of the substrate 16 a of the orbiting scroll 16 slides on the thrust plate 34.

  Further, a rotation prevention mechanism 36 is disposed between the back surface 16 c of the substrate 16 a of the movable scroll 16 and the pedestal portion 4 a of the front casing 4. The rotation prevention mechanism 36 prevents the rotation of the movable scroll 16 without hindering the revolving turning motion of the movable scroll 16 relative to the fixed scroll 14.

  According to the compressor 1 described above, as the drive shaft 8 rotates, the movable scroll 16 revolves without rotating while sliding the back surface 16 c on the thrust plate 34. Thereby, the refrigerant sucked into the suction chamber 20 from the return path of the refrigerant circulation path forms the compression chamber 18, and the refrigerant in the compression chamber 18 is compressed while being moved toward the center of the scroll unit 6, and then discharged. It is discharged into the discharge chamber 22 through the hole 24 and sent out from the discharge chamber 22 to the forward path of the refrigerant circulation path.

  FIG. 2 is a plan view of the rotation prevention mechanism 36 viewed from the direction AA of FIG. As shown in FIG. 2, the rotation prevention mechanism 36 is a pin and ring type mechanism having four sets of rotation prevention pins 38 and a restriction ring 40. The pin 38 is press-fitted and fixed to the pedestal 4 a of the front casing 4 and has a protruding portion 38 a that protrudes toward the substrate 16 a of the movable scroll 16. The ring 40 is press-fitted and fixed in a receiving hole 42 formed in the back surface 16 c of the substrate 16 a of the movable scroll 16.

  Both the pin 38 and the ring 40 are made of a high hardness material such as SUJ2 (high carbon chromium bearing steel). The protruding portion 38 a of the pin 38 is loosely fitted in the ring 40 in the radial direction, and is slid on the inner peripheral surface 40 a of the ring 40 as the movable scroll 16 revolves with respect to the fixed scroll 14.

  FIG. 3 is an enlarged cross-sectional view of the pair of rings 40 and the accommodation holes 42 shown in FIG. 2 as seen from the direction BB in FIG. As shown in FIG. 3, a clearance space 44 is secured in the opening 42 a of the accommodation hole 42. The escape space 44 is not in contact with a part of the outer peripheral surface 40 b of the ring 40, and when the protrusion 38 a of the pin 38 slides on the inner peripheral surface 40 a of the ring 40, the escape space 44 expands due to elastic deformation of the ring 40. Is acceptable.

The escape space 44 is formed by expanding the inner peripheral surface 42b of the opening 42a of the accommodation hole 42 over the entire circumference.
FIG. 4 shows an enlarged relief space 44 formed on the outer peripheral surface 16d side of the substrate 16a of the movable scroll 16 shown in FIG. As shown in FIG. 4, the inner peripheral surface 42 b of the accommodation hole 42 includes a press-fit surface portion 46, a tapered surface portion 48, and a counterbore surface portion 50.

  The press-fit surface portion 46 is an annular surface on which the ring 40 is press-fitted and fixed. The tapered surface portion 48 is an annular surface that extends from the press-fit surface portion 46 toward the opening end 42 c of the opening 42 a of the accommodation hole 42 and is inclined in a direction in which the diameter of the accommodation hole 42 is increased. The counterbore surface portion 50 is an annular surface that extends from the tapered surface portion 48 toward the opening end 42 c of the opening portion 42 a of the accommodation hole 42 and has the same diameter as the largest diameter portion 48 a of the tapered surface portion 48.

That is, the escape space 44 forms an annular region formed in the accommodation hole 42 between the outer peripheral surface 40 b of the ring 40 and the tapered surface portion 48 and the counterbore surface portion 50 of the inner peripheral surface 42 b of the accommodation hole 42.
By forming the tapered surface portion 48 on the inner peripheral surface 42 b of the receiving hole 42, it is possible to easily perform press-fitting work when the ring 40 is press-fitted into the receiving hole 42 using a jig. On the other hand, by forming the counterbore surface portion 50 on the inner peripheral surface 42 b of the accommodation hole 42, it is possible to promote the reduction in the diameter of the substrate 16 a of the movable scroll 16 and the downsizing of the compressor 1 and the scroll unit 6.

  Specifically, as shown in FIG. 3, the receiving hole 42 must be formed in the vicinity of the outer peripheral surface 16 d of the substrate 16 a of the movable scroll 16 by reducing the diameter of the movable scroll 16. For this reason, by making the part facing the opening end 42c of the escape space 44 the counterbore surface portion 50, the back surface 16c of the substrate 16a of the movable scroll 16 can be secured in the vicinity of the outer peripheral surface 16d. Therefore, the escape space 44 can be formed while realizing a smooth revolution turning of the movable scroll while suppressing the inclination of the movable scroll with respect to the fixed scroll while reducing the diameter of the movable scroll 16.

  As shown in FIG. 4, when forming the escape space 44, the accommodation hole 42 has an overall length of the ring 40 in the height direction Y of the ring 40: the overall length L1 of the ring and a length in the height direction Y of the escape space 44: the escape space. Length L2, press-fitting length of ring 40 in height direction Y: ring press-fitting length L3, depth in height direction Y in which tapered surface portion 48 and counterbore surface portion 50 are processed by receiving hole 42: receiving hole processing depth D1 Depth in the height direction Y from the open end 42 c of the accommodation hole 42 to the pin 38: ring press-fit depth D 2, the largest diameter portion 48 a (or counterbore surface portion 50) of the tapered surface portion 48 and the ring 40 of the pin 38. Each dimension such as a gap in the radial direction X: a clearance gap G1 is defined.

On the other hand, the ring 40 is formed to have an expansion allowance portion 52 that defines a clearance space length L2 and a press-fit portion 54 that defines a ring press-fit length L3.
The following are examples of numerical values of some dimensions defined in FIG.
・ Ring total length L1: 5mm
・ Relief space length L2: 1 mm
・ Escape gap G1: 0.1 mm

  As is apparent from these data, it has been found by experiments of the inventors that the ratio of the clearance space length L2 to the ring length L1 is preferably 20% at maximum. If this ratio exceeds 20%, the ring press-fitting length L3 is insufficient, and the ring 40 cannot be firmly supported in the accommodation hole 42. Therefore, the ring 40 may drop from the accommodation hole 42 as the compressor 1 is operated. .

  It has also been found that the clearance gap G1 is preferably set to about 0.1 mm. It has also been found that the ring press-fit depth D2 is preferably set shallower (smaller) than in the prior art. The reason for the preferable ranges of the clearance gap G1 and the ring press-fit depth D2 will be described in detail below with reference to FIGS.

  FIG. 5 shows a state in which the base portion 38 b located in the vicinity of the thrust plate 34 of the projecting portion 38 a of the pin 38 temporarily contacts the edge of the opening 40 c of the ring 40. In this state, the press-fit portion 54 of the ring 40 is maintained in press-fit to the press-fit surface portion 46 of the accommodation hole 42.

  In FIG. 5, an action point P1 at which a force F based on the turning load of the movable scroll 16 (the pressing force of the movable scroll 16 against the fixed scroll 14) acts on the pin 38, and the pin press-fitted and fixed to the pedestal 4a of the front casing 4 38 defines a support point P2 of the pin 38 exposed from the pedestal portion 4a. The action point P1 is a part where the root part 38b hits an edge of the opening 40c of the ring 40, and the support point P1 and the action point P2 are separated by a distance Dm.

  The distance Dm is determined according to the thickness T of the thrust plate 34, the ring press-fit depth D2, and the like. When the orbiting scroll 16 revolves at a high speed and the orbiting load of the orbiting scroll 16 increases due to the operating conditions required for the compressor 1, the force F acting on the action point P1 increases, and consequently the force F and the distance Dm. The moment M of the force acting on the pin 38 multiplied by is also increased. As the moment M increases, the protrusion 38 a of the pin 38 is elastically deformed, the axis Lp of the protrusion 38 a of the pin 38 intersects the height direction Y of the ring 40, and the pin 38 is inclined with respect to the height direction Y. Inclined at α.

  As described above, the ring press-fit depth D2 affects the distance Dm, the moment M, the inclination angle α, and the expansion angle β of the ring 40 described later. Therefore, as described above, the ring press-fit depth D2 is set to be shallower than that of the prior art, so that the distance Dm and thus the moment M are made smaller than before, and the inclination angle α of the pin 38 with respect to the height direction Y is made smaller. Therefore, the expansion angle β of the ring 40 can be suitably controlled.

  FIG. 6 shows a state where the inclined pin 38 is further pressed against the ring 40 from the state of FIG. 5 and the ring 40 is expanded and deformed. When the pin 38 is pressed against the ring 40 with a force against the rigidity of the ring 40 from a temporary edge contact state of the pin 38 with respect to the ring 40, the escape space 44 is secured in the accommodation hole 42. Of the ring 40 has an expansion angle β with respect to the height direction Y of the ring 40 and elastically deforms in the direction in which the ring 40 expands.

  Even when the ring 40 is elastically deformed, the press-fitting portion 54 of the ring 40 into the press-fit surface portion 46 of the accommodation hole 42 is maintained. Further, since the inclination angle α of the pin 38 shown in FIG. 5 is equal to the expansion angle β, the outer peripheral surface 38c of the projecting portion 38a of the inclined pin 38 is in contact with the inner peripheral surface 40a of the ring 40 in the expansion allowing portion 52. It is slid over the whole area in the height direction Y.

  The expansion angle β of the ring 40 is determined so that the expansion allowance portion 52 becomes the counterbore surface portion 50 even if the expansion angle β is the largest, from the assumed turning load of the movable scroll 16, the elastic coefficient of the pin 38 and the ring 40, etc. It is set in advance to a predetermined range in which the ring 40 is not contacted and the expansion deformation of the ring 40 is not restricted. As described above, as a result of the inventor's study on the expansion angle β that can secure the clearance space 44 after the expansion deformation of the ring 40, the clearance gap G1 before the expansion deformation of the ring 40 is 0. It has been found preferable to set it to about 1 mm.

  As described above, in the present embodiment, the opening 42 a of the accommodation hole 42 is allowed to expand with the elastic deformation of the ring 40 when the protruding portion 38 a of the pin 38 slides on the inner peripheral surface 40 a of the ring 40. A clearance space 44 is secured. Thereby, irrespective of the driving | running condition of the compressor 1, both durability and silence of the compressor 1 can be improved. According to the endurance test conducted by the inventor, the wear amount of the pin is actually reduced to 50% to 60% as compared with the conventional case.

  Specifically, when the turning load of the movable scroll 16 is relatively small, the axis Lp of the protruding portion 38a of the pin 38 is parallel to the height direction Y of the ring 40 and the pin 38 does not tilt. For this reason, even if the protruding portion 38a of the pin 38 slides on the inner peripheral surface 40a of the ring 40, the ring 40 maintains its shape with its own rigidity and does not elastically deform. Therefore, since the contact area of the pin 38 with the ring 40 can be ensured, the contact surface pressure of the pin 38 with the ring 40 can be reduced, and thus wear and noise of the pin 38 can be suppressed.

  On the other hand, when the turning load of the movable scroll 16 is relatively large, the axis Lp of the protruding portion 38a of the pin 38 intersects the height direction Y of the ring 40, and the pin 38 is inclined. However, since the turning load of the movable scroll 16 is large, when the protrusion 38 a of the pin 38 slides on the inner peripheral surface 40 a of the ring 40, the pin 38 is pressed against the ring 40 with a force that resists the rigidity of the ring 40.

  For this reason, the ring 40 is elastically deformed in the direction in which the ring 40 expands so as to follow the inclination of the pin 38. Therefore, even when the pin 38 is inclined, it is possible to suppress the edge contact of the pin 38 with the ring 40 and to secure the contact area of the pin 38 with the ring 40, and the contact surface pressure of the pin 38 with respect to the ring 40 is increased. As a result, wear and noise of the pin 38 can be suppressed.

  The escape space 44 is formed by expanding the inner peripheral surface 42b of the opening 42a of the accommodation hole 42 over the entire circumference. Thereby, since the relief space 44 can be formed in the accommodation hole 42 by a simple process, this contributes to the productivity improvement of the compressor 1. In addition, the ring 40 can be maintained in a perfect circle shape when viewed from the height direction Y regardless of the operating state of the compressor 1. Therefore, both durability and quietness of the compressor 1 can be further effectively improved as compared with the case where the escape space 44 is partially formed in the accommodation hole 42.

Further, since the tapered surface portion 48 is formed on the inner peripheral surface 42b of the accommodation hole 42, the press-fitting work when the ring 40 is press-fitted into the accommodation hole 42 using a jig can be easily performed. The productivity of 1 is improved.
Further, by forming the counterbore surface portion 50 on the inner peripheral surface 42b of the accommodation hole 42, while securing the back surface 16c of the substrate 16a of the movable scroll 16 in the vicinity of the outer peripheral surface 16d of the movable scroll 16 when forming the accommodation hole 42, The diameter of the movable scroll 16 can be reduced. Therefore, the inclination of the movable scroll 16 with respect to the fixed scroll 14 can be suppressed, and the miniaturization of the compressor 1 can be promoted while realizing the smooth revolution turning of the movable scroll 16.

  Further, the clearance space length L2 that is the length of the clearance space 44 in the height direction Y of the ring 40 is defined as a maximum of 20% of the total ring length L1 that is the total length of the ring 40 in the height direction Y of the ring 40. . Thereby, even if the ring 40 is elastically deformed in the expanding direction, the press-fitting of the ring 40 into the 42 press-fitting surface portion 46 of the accommodation hole can be reliably maintained. Accordingly, the ring 40 is not firmly supported in the accommodation hole 42, and the risk of the ring 40 dropping off from the accommodation hole 42 with the operation of the compressor 1 is eliminated, and the reliability of the compressor 1 can be improved. .

The present invention is not limited to the above embodiment, and various modifications are possible.
For example, the pin 38 may be erected from the substrate 16 a of the movable scroll 16, and the accommodation hole 42 may be provided in the pedestal portion 4 a of the front casing 4.
Moreover, the pin 38 and the ring 40 which comprise the autorotation prevention mechanism 36 are not limited to four sets.

  In the present embodiment, the escape space 44 is formed by expanding the inner peripheral surface 42b of the opening 42a of the accommodation hole 42 over the entire circumference. However, the relief space 44 may be partially formed only in a portion where the pin 38 is inclined and slid on the inner peripheral surface 42b of the accommodation hole 42. In this case, although the shape of the accommodation hole 42 and the ring 40 cannot be maintained in a perfect circle shape, both the durability and quietness of the compressor 1 can be improved at least as compared with the conventional case.

  Further, if the back surface 16c of the substrate 16a of the movable scroll 16 can be secured in the vicinity of the outer peripheral surface 16d of the movable scroll 16, the counterbore surface portion 50 is eliminated, and the escape space 44 is formed only by the tapered surface portion 48 facing the opening end 42c. May be. Even in this case, both the durability and quietness of the compressor 1 can be improved at least as compared with the conventional case.

  Moreover, in the said embodiment, the engine-driven scroll compressor 1 incorporated in the vehicle air conditioner was demonstrated. However, the present invention can be applied to scroll-type fluid machines in general such as electric motor-driven scroll compressors and compressors or expanders in various fields using various working fluids.

1 Scroll type fluid machine (scroll compressor)
4 Front casing (casing)
4a Pedestal part 14 Fixed scroll 16 Movable scroll 16a Substrate 16b Spiral wall 36 Rotation prevention mechanism 38 Rotation prevention pin 38a Protrusion part 40 Restriction ring 40a Inner peripheral surface 40b of regulation ring Outer surface of regulation ring 42 Accommodation hole 42a 42b Inner circumferential surface of receiving hole 44 Escape space 46 Press-fit surface portion 48 Tapered surface portion 48a Maximum diameter portion 50 Counterbore surface portion

Claims (2)

A scroll type fluid machine provided with a rotation prevention mechanism for preventing the rotation of the movable scroll without disturbing the revolution orbiting movement of the movable scroll with respect to the fixed scroll fixed to the casing,
The rotation prevention mechanism is
A substrate on which a spiral wall of the movable scroll is erected, and a rotation prevention pin that is erected from any one of the pedestal portions of the casing that are positioned facing the substrate;
A regulation ring that is press-fitted into a receiving hole that is drilled in the other of the substrate and the pedestal, and in which the rotation prevention pin is loosely fitted,
In the opening of the accommodation hole, when the projecting portion of the rotation prevention pin slides on the inner peripheral surface of the restriction ring, a clearance space is secured that allows expansion due to elastic deformation of the restriction ring ,
The escape space is formed by expanding the inner circumferential surface of the opening of the accommodation hole over the entire circumference,
The inner peripheral surface of the accommodation hole includes a press-fit surface portion into which the restriction ring is press-fitted and fixed, and a tapered surface portion that extends from the press-fit surface portion toward an opening end of the opening portion and is inclined in a direction of increasing the diameter of the accommodation hole. And a counterbore surface portion extending from the tapered surface portion toward the opening end and having the same diameter as the largest diameter portion of the tapered surface portion,
The escape fluid space is a scroll type fluid machine formed between an outer peripheral surface of the regulating ring, the tapered surface portion, and the counterbore surface portion . The relief space length in the height direction of the regulating ring clearance space, the a maximum of 20% of the ring the entire length in the height direction of the regulating ring, a scroll type fluid machine according to claim 1.

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