JP2012062820A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain generation of noise and vibration, while improving durability by surely and smoothly making lubricating oil flow, in a scroll compressor.SOLUTION: A crank pin 68 is arranged on an end surface of a support arranged in the end part of a rotary shaft on the rotary shaft for constituting the scroll compressor, and the crank pin 68 is inserted into an eccentric hole 70 of a bush 52. A locking groove 74 having first and second flat parts 78 and 80 is formed in the end part of the crank pin 68, and a locking ring 84 having first and second straight line parts 90 and 92 is installed in the locking groove 74. The locking ring 84 faces in its opening part 86 to an oil passage 76 constituted of a cutout part of the crank pin 68 and the eccentric hole 70, and regulates relative rotational displacement to the crank pin 68 under the engaging action of the first and second flat parts 78 and 80 and the first and second straight line parts 90 and 92.

Description

  The present invention relates to a scroll type compressor, and more particularly to a scroll type compressor that compresses fluid inside a compressor by turning a movable scroll with respect to a fixed scroll.

  Generally, a scroll type compressor has a fixed scroll, a fixed scroll having a spiral fixed wall upright on the fixed plate, and a movable plate and a spiral movable wall upright on the movable plate engaged with the fixed wall. A movable scroll arranged so as to be aligned is provided inside the housing, and the movable scroll is pivoted via an eccentric crank pin to thereby fix the fixed wall of the fixed scroll, the movable wall of the movable scroll, the fixed plate, and the movable plate. The compression chamber formed between them is gradually moved from the outer peripheral portion to the central portion to compress the refrigerant (see Patent Document 1).

  By the way, in such a scroll compressor, the thing of the structure provided with the turning radius variable mechanism which makes the turning radius of a movable scroll variable may be used. By providing this turning radius variable mechanism, it is possible to obtain effects such as prevention of breakage of the fixed wall and the movable wall at high loads due to liquid compression and the like, and improvement in contact between the fixed wall and the movable wall (for example, , See Patent Document 1).

  In the scroll compressor, in order to improve the lubricity between the crank mechanism, in particular, the bush and the crankpin, an oil passage is formed between the bush and the crankpin, and the lubricating oil is circulated through the oil passage. Lubrication may be performed (see, for example, Patent Document 2).

JP 2010-150944 A JP 7-317671 A

  However, in general, in a scroll compressor having a turning radius variable mechanism as disclosed in Patent Document 1, the crank pin is formed in a cylindrical shape. When an oil passage as disclosed in Patent Document 2 is formed for this crank pin, a locking ring for engaging the crank pin and the bush rotates while the compressor is operating, and the engagement If the opening portion of the oil passage is blocked by the ring portion of the stop ring, the fluidity of the lubricating oil flowing through the oil passage is lowered, and the expected lubrication performance may not be obtained.

  The present invention has been made in consideration of the above-mentioned problems, and it is possible to improve durability by reliably and smoothly circulating lubricating oil, and to suppress generation of noise and vibration. It is an object of the present invention to provide a scroll type compressor that can be used.

In order to achieve the above object, the present invention provides a housing, a fixed scroll provided in the housing, a movable scroll meshed with the fixed scroll, and a driving source provided in the housing. A rotating shaft that rotates in a rotating manner, a crank pin that is eccentric with respect to the axis of the rotating shaft, a bush that has a hole through which the crank pin is inserted, and that swings and displaces the movable scroll, and the crank pin as a center. A swing link mechanism for swinging the movable scroll with a swing radius by swinging the bush, and a mechanism for restricting a relative displacement along the axial direction of the crankpin that is attached to an end of the crankpin. In a scroll compressor with a stop ring,
An oil passage through which lubricating oil flows is provided between the bush and the crank pin, and the locking ring has an opening for mounting to the crank pin, and the locking ring is the crank pin. And a rotation restricting means for restricting rotation, wherein the opening faces the oil passage and restricts the relative rotational displacement of the locking ring with respect to the crank pin.

  According to the present invention, the locking ring is attached to the crank pin, and the opening is disposed so as to face the oil passage that is provided between the bush and the crank pin and through which the lubricating oil flows, and is locked by the rotation restricting means. The ring restricts rotational displacement with respect to the crank pin.

  Accordingly, since the locking ring does not rotate with respect to the crankpin, the opening can always be arranged at a position facing the oil passage, and accordingly, the oil passage is blocked by the locking ring. It is avoided that the plug is blocked, and the lubricating oil can be reliably and stably supplied to the bush side through the oil passage. As a result, the lubrication between the crankpin and the bush can be performed reliably and stably, the durability of the scroll compressor can be improved, and the generation of noise and vibration due to insufficient lubrication can be suppressed. .

Further, the rotation restricting means has a flat portion that is recessed with respect to the outer peripheral surface at the end of the crankpin, and a groove portion to which the locking ring is attached,
A straight portion formed on the locking ring and engaged with the flat portion;
It is good to comprise.

  Furthermore, the rotation restricting means may be a convex portion provided on the end surface of the bush and abutting against the opening of the locking ring.

  Furthermore, the convex portion may have a passage through which lubricating oil supplied through the oil passage flows to the end face.

  According to the present invention, the following effects can be obtained.

  That is, with the crankpin inserted into the hole of the bush, a locking ring is attached to the end of the crankpin, and the relative rotational displacement of the locking ring with respect to the crankpin is regulated by the rotation regulating means. Therefore, the locking ring is prevented from being rotationally displaced relative to the crank pin, and the oil passage formed between the locking ring and the bush is prevented from being blocked by the locking ring. it can. As a result, the lubricating oil supplied through the oil passage can reliably and stably lubricate between the crankpin and the bush, and the durability of the scroll compressor can be improved, and noise and noise caused by insufficient lubrication can be improved. Generation of vibration can be suppressed.

1 is a partially omitted vertical sectional view of a scroll compressor according to an embodiment of the present invention. It is an expanded sectional view which shows the crankpin vicinity in the scroll compressor of FIG. It is a front view of the crankpin and bush of the scroll compressor shown in FIG. 4A is a front view of a bush according to a modification, and FIG. 4B is a cross-sectional view taken along the line IVB-IVB in FIG. 4A.

  A preferred embodiment of a scroll compressor according to the present invention will be described in detail below with reference to the accompanying drawings.

  In FIG. 1, reference numeral 10 indicates a scroll compressor according to an embodiment of the present invention.

  As shown in FIG. 1, the scroll compressor 10 includes a front housing 12 formed in a lid shape and a rear housing 14 formed in a cup shape.

  In the upper part of the rear housing 14, for example, a suction port 16 for introducing a gas (see FIG. 2) made of a refrigerant gas or the like into the interior is formed. The suction port 16 opens to the outer peripheral surface of the rear housing 14 and penetrates toward the center of the rear housing 14 to communicate with the inside.

  Further, at the upper part of the rear housing 14, a discharge port 18 is formed for discharging the compressed gas compressed by the scroll compressor 10 to, for example, a refrigerant circulation system (not shown). The rear housing 14 is provided with a plurality of attachment portions 20 for attaching the scroll compressor 10 to, for example, an engine or an external device (not shown). Note that the scroll compressor 10 is disposed and fixed horizontally, for example, such that the axes of the front housing 12 and the rear housing 14 are substantially parallel to the ground.

  Then, a fixed scroll 22 and a movable scroll 24 that pivots with respect to the fixed scroll 22 are inserted into the rear housing 14 from the opened one end side.

  The fixed scroll 22 includes a fixed side substrate portion 26 including an outer peripheral edge connected to the rear housing 14, and a fixed side spiral wall 28 erected in a spiral shape from the fixed side substrate portion 26 to the movable scroll 24 side. Have

  In addition, a gas discharge chamber 30 communicating with the discharge port 18 is formed between the back surface of the fixed scroll 22 and the rear housing 14, and a gas compression chamber, which will be described later, is formed at a substantially central portion of the fixed side substrate portion 26. A compressed gas outlet hole 36 that communicates from 34 to the gas discharge chamber 30 is formed. The fixed-side board portion 26 is connected to the rear housing 14 by a plurality of fastening bolts 38.

  Furthermore, the compressed gas outlet hole 36 is closed on the back surface of the fixed-side substrate portion 26, and when the compressed gas compressed in the gas compression chamber 34 reaches a predetermined pressure, it opens to the gas discharge chamber 30. A discharge valve 40 for deriving the compressed gas is provided.

  As shown in FIG. 1, the movable scroll 24 is erected in a spiral shape from the movable side substrate portion 42 to the fixed scroll 22 side (arrow A direction) from the movable side substrate portion 42, and the fixed side spiral wall And a movable spiral wall 44 that meshes with 28.

  In the rear housing 14, the movable-side spiral wall 44 is disposed so as to be on the fixed scroll 22 side (arrow A direction), and the fixed-side substrate portion 26 and the fixed-side spiral wall 28 that constitute the fixed scroll 22, A gas compression chamber 34 is formed by the movable side substrate portion 42 and the movable side spiral wall 44 constituting the movable scroll 24. In order to seal the gas compression chamber 34, a sealing member 46 is slidably in contact with the movable side substrate portion 42 and the fixed side substrate portion 26 at the respective ends of the fixed side spiral wall 28 and the movable side spiral wall 44. Is installed.

  In addition, a circular recess 48 opened on the front side is formed in the movable side substrate portion 42 at the center portion, and a bush 52 is fitted into the inside thereof via a swivel bearing 50.

  The drive unit 54 includes a rotary shaft 56, a bush 52 connected to an end of the rotary shaft 56, first and second bearings 58 and 60 that rotatably support the rotary shaft 56, and the bush 52. The rotary shaft 56 includes a rotary bearing 50 that is rotatably supported. The rotary shaft 56 has a shaft portion 62 that is one end of the rotary shaft 56 inserted into an opening provided at an end portion of the front housing 12, and is rotatable via a second bearing 60. Supported by In addition, a sealing member 64 for sealing the gas suction chamber between the front housing 12 is fitted on the outer peripheral side of the shaft portion 62.

  On the other hand, the other end of the rotary shaft 56 is provided with a support body 66 whose diameter is increased with respect to the shaft portion 62. The support body 66 is rotated by being inserted into a first bearing 58 provided in the through hole. It is supported freely. The first bearing 58 is held inside the front housing 12. A crankpin 68 that is eccentric with respect to the axis is provided on the end surface of the support 66.

  As shown in FIGS. 1 to 3, the crankpin 68 is formed in a shaft shape having a substantially constant diameter, is formed so as to protrude from the end surface of the support 66 by a predetermined length, and the shaft center of the bush 52. Is inserted into the eccentric hole 70 which is eccentric with respect to. In addition, a cutout portion 72 is formed on the outer peripheral surface of the crankpin 68, a part of which is cut out in a plane shape in cross section, and in the vicinity of the tip portion of the crankpin 68, the outer peripheral surface has a substantially rectangular cross section. A more recessed locking groove 74 is formed along the outer peripheral surface.

  When the crank pin 68 is inserted into the eccentric hole 70, a gap formed between the notch 72 and the inner peripheral surface of the eccentric hole 70 becomes an oil passage 76 through which the lubricating oil flows. Specifically, the oil passage 76 is formed in a substantially semicircular cross section from a cutout portion 72 formed in a cross-sectional planar shape and a part of the inner peripheral surface of the eccentric hole 70 facing the cutout portion 72 (see FIG. 3).

  The locking groove 74 is formed at a position exposed to the outside of the eccentric hole 70 when the crank pin 68 is inserted into the eccentric hole 70, and is a linear first and second flat surface that is substantially orthogonal to the notch portion 72. The first and second flat portions 78 and 80 are formed on the opposite side of the notch 72 with respect to the center of the crank pin 68, and the circular arc portion 82 is joined to the first and second flat portions 78 and 80. The first flat portion 78 and the second flat portion 80 are formed substantially in parallel with the center of the crankpin 68 interposed therebetween. Note that chamfers are provided between the first and second flat portions 78 and 80 and the cutout portion 72, respectively. Then, after the crank pin 68 is inserted into the eccentric hole 70 of the bush 52, the locking ring 84 is attached to the locking groove 74. As a result, the bush 52 can rotate around the crank pin 68 in a state where the locking pin 84 prevents the crank pin 68 from coming off in the axial direction (directions of arrows A and B).

  The locking ring 84 is formed in a substantially U-shaped cross section having an opening 86, and extends from the curved portion 88 engaged with the arc portion 82 in the locking groove 74 and both ends of the curved portion 88. It consists of existing linear first and second linear portions 90 and 92. In addition, the 1st linear part 90 and the 2nd linear part 92 are formed substantially parallel.

  Then, after disposing the locking ring 84 so that the opening 86 formed between the tip of the first straight portion 90 and the tip of the second straight portion 92 is on the crank pin 68 side, 86, the curved portion 88 is attached to the arc portion 82, and the first and second straight portions 90 and 92 are attached to the first and second flat portions 78 and 80, respectively. The

  As a result, relative rotation displacement of the locking ring 84 relative to the crank pin 68 is restricted under the engagement action of the first and second linear portions 90 and 92 and the first and second flat portions 78 and 80. . That is, the first and second straight portions 90 and 92 of the locking ring 84 and the first and second flat portions 78 and 80 of the crank pin 68 are relatively rotated with respect to the crank pin 68 of the locking ring 84. It functions as a rotation restricting means capable of restricting displacement.

  The locking ring 84 is mounted so that the opening 86 faces the notch 72 of the crankpin 68 and does not cover the oil passage 76 formed between the eccentric hole 70 and the notch 72 ( (See FIG. 3). In other words, the one end side and the other end side of the bush 52 are reliably and preferably communicated with each other through the oil passage 76 and the opening 86.

  The bush 52 is turned so as to be able to swing by the rotating shaft 56 by inserting the crank pin 68 into the eccentric hole 70, and thereby the movable scroll 24 is turned while changing the turning radius. A balance weight 94 is mounted near the base of the crankpin 68 via the bush 52.

  A thrust plate 96 is provided between the movable side substrate portion 42 of the movable scroll 24 and the support surface formed inside the front housing 12 so as to slidably support the movable scroll 24 with the sliding contact surface.

  On the other hand, a pulley 100 is attached to the outer periphery of the opening of the front housing 12 via a third bearing 98. A rotational force is transmitted to the pulley 100 from a rotational drive source such as an engine (not shown) via a belt or the like, and the rotational force is transmitted to or disconnected from the rotational shaft 56 by the on / off operation of the electromagnetic clutch 102.

  The scroll compressor 10 according to the embodiment of the present invention is basically configured as described above. Next, the operation, action, and effect thereof will be described.

  First, when a rotational force is transmitted to the rotary shaft 56 under the operation of the electromagnetic clutch 102, the support 66 is rotated through the first bearing 58, whereby the crank pin 68 fixed to the support 66 is obtained. Swivels in an eccentric state with respect to the axis of the rotary shaft 56. As a result, the bush 52 rotates, and the movable scroll 24 slidably supported by the thrust plate 96 turns with respect to the fixed scroll 22.

  The gas supplied from the suction port 16 is introduced into the rear housing 14 and is formed between the fixed-side spiral wall 28 in the fixed scroll 22 and the movable-side spiral wall 44 in the movable scroll 24. A part of the gas is introduced to the drive unit 54 side, and the lubricating oil contained in the gas is supplied to the shaft portion 62 of the rotary shaft 56, for example.

  The lubricating oil circulates from the support 66 in the rotary shaft 56 to the fixed scroll 22 side (in the direction of arrow A) along the notch 72 of the crank pin 68 and then circulates through the oil passage 76 to the locking ring 84 side. Thereafter, the ink is discharged from the opening 86 of the eccentric hole 70 and flows along the end surface of the bush 52. Thereby, the lubrication between the crankpin 68 and the bushing 52 is reliably performed under the action of supplying the lubricating oil. At this time, the lubricating oil flows to the end face side (arrow A direction) of the bushing 52 through the opening 86 of the locking ring 84, and it is avoided that the flow is blocked by the opening 86.

  On the other hand, the gas compression chamber 34 formed between the fixed-side spiral wall 28 in the fixed scroll 22 and the movable-side spiral wall 44 in the movable scroll 24 advances gradually from the outer peripheral portion to the central portion, and the sealing member 46 is sealed. The gas introduced into the gas suction chamber under the stopping action is gradually compressed. Thereafter, the compressed gas that has been compressed is led out from the compressed gas outlet hole 36 to the gas discharge chamber 30 and is discharged through the discharge port 18 to a refrigerant circulation system (not shown).

  As described above, in the present embodiment, in the crank pin 68 provided with the cutout portion 72 having a planar cross section on the outer peripheral surface, the locking groove 74 having the first and second flat portions 78 and 80 at the tip thereof. And a locking ring 84 having first and second straight portions 90 and 92 engaged with the first and second flat portions 78 and 80 is mounted on the locking groove 74. . Thus, in the state where the crank pin 68 is inserted into the eccentric hole 70 of the bush 52, the axial displacement of the locking ring 84 is restricted by the locking ring 84, and the locking ring 84 is relative to the crank pin 68. The rotational displacement is prevented. The locking ring 84 is mounted so that the opening 86 faces the notch 72 of the crank pin 68.

  Accordingly, since the locking ring 84 does not rotate with respect to the crank pin 68, the oil passage 76 formed between the notch 72 and the eccentric hole 70 is blocked by the locking ring 84. Thus, the lubricating oil can be reliably and stably supplied to the end face side of the bush 52 through the oil passage 76 and the opening 86. As a result, the lubrication between the crankpin 68 and the bushing 52 can be performed reliably and stably, the durability of the scroll compressor 10 can be improved, and the generation of noise and vibration due to insufficient lubrication can be suppressed. It becomes possible to do.

  Further, like the bush 52a shown in FIGS. 4A and 4B, a stopper wall 104 that protrudes from the end surface thereof and is disposed outside the opening 86 of the eccentric hole 70 is provided, and the opening 86 of the locking ring 84a is provided. May be brought into contact with the stopper wall 104. In this case, the locking ring 84a can be a general ring having a substantially C-shaped cross section that does not have the first and second straight portions 90 and 92, and the tip of the crankpin 68a. It is possible to restrict the rotational displacement of the locking ring 84a without providing the first and second flat portions 78 and 80 also in the locking groove 74a formed in the portion.

  The stopper wall 104 has a groove 106 that protrudes from the end surface of the bush 52a by a predetermined height and is recessed in a V-shaped cross section at a position that is in a straight line with the center of the eccentric hole 70. The groove 106 is formed in the bush 52a. It extends toward the outer circumferential direction. Therefore, for example, when the lubricating oil is led out from the oil passage 76 constituted by a part of the eccentric hole 70, the lubricating oil is supplied along the groove portion 106 toward the outer peripheral side of the bush 52a. Become.

  The scroll compressor according to the present invention is not limited to the above-described embodiment, and can of course have various configurations without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 10 ... Scroll type compressor 12 ... Front housing 14 ... Rear housing 22 ... Fixed scroll 24 ... Movable scroll 26 ... Fixed side board | substrate part 28 ... Fixed side spiral wall 42 ... Movable side board part 44 ... Movable side spiral wall 50 ... Swivel bearing 52, 52a ... Bush 54 ... Drive 56 ... Rotating shaft 62 ... Shaft 66 ... Support 68 ... Crank pin 70 ... Eccentric hole 72 ... Notch 74, 74a ... Lock groove 76 ... Oil passage 78 ... First flat part 80 ... 2nd flat part 82 ... Arc part 84, 84a ... Locking ring 86 ... Opening part 88 ... Curved part 90 ... 1st linear part 92 ... 2nd linear part 100 ... Pulley 102 ... Electromagnetic clutch 104 ... Stopper wall 106 ... Groove

Claims (4)

A housing; a fixed scroll provided in the housing; a movable scroll meshed with the fixed scroll; a rotary shaft provided in the housing and rotating under a drive action of a drive source; and an axis of the rotary shaft A crank pin eccentric with respect to the shaft, a bush having a hole through which the crank pin is inserted, and a swinging displacement of the movable scroll, and swinging the bush around the crank pin to turn the movable scroll In a scroll compressor comprising a swing link mechanism for turning the radius variable, and a locking ring that is attached to an end of the crankpin and restricts a relative displacement along an axial direction of the crankpin with respect to the bush.
An oil passage through which lubricating oil flows is provided between the bush and the crank pin, and the locking ring has an opening for mounting to the crank pin, and the locking ring is the crank pin. And a rotation restricting means for restricting rotation, wherein the opening faces the oil passage and restricts relative rotational displacement of the locking ring with respect to the crank pin. Mold compressor. The scroll compressor according to claim 1, wherein
The rotation restricting means is recessed with respect to the outer peripheral surface at an end portion of the crankpin, and has a flat portion, and a groove portion to which the locking ring is attached,
A straight portion formed on the locking ring and engaged with the flat portion;
A scroll compressor characterized by comprising: The scroll compressor according to claim 1, wherein
The scroll compressor according to claim 1, wherein the rotation restricting means is a convex portion provided on an end surface of the bush and abutting against an opening of the locking ring. The scroll compressor according to claim 3, wherein
The scroll compressor according to claim 1, wherein the convex portion has a passage through which lubricating oil supplied through the oil passage is circulated to the end face.

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