JP2008057499A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor improving assembling property of a thrust bearing. <P>SOLUTION: The compressor comprises: a bearing hole 14 to which a drive shaft 10 is journaled; the thrust bearing 16 restricting axial movement of the drive shaft 10 while being held by the bearing hole 14, and having projected pieces 16b radially projected from the outer circumference of the thrust bearing; insertion slits 61, which are formed to the bearing hole 14, and in which projected pieces 16b of the thrust bearing can be inserted from an axial direction; stopper grooves 6, which are formed to the bearing hole 14 to receive the projected pieces 16b of the thrust bearing at positions circumferentially shifted from the insertion slits 14 and thereby to restrict axial movement of the thrust bearing 16; a detent member 17 inserted into and engaged with the insertion slits 61, in a state where the projected pieces 16b of the thrust bearing are positioned into the stopper grooves 63, so as to restrict rotation of the thrust bearing 16. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a compressor.

  For example, a compressor disclosed in Patent Document 1 includes a housing having a crank chamber, a cylinder bore, a suction chamber, and a discharge chamber, and a drive rotatably supported in the crank chamber supported by a pair of bearing holes provided across the crank chamber. The shaft includes a piston that is reciprocally movable in the cylinder bore, and a conversion mechanism that is attached to the drive shaft and converts the rotation of the drive shaft into the reciprocating motion of the piston. As the drive shaft rotates, the piston reciprocates within the cylinder bore. As the piston reciprocates, the medium to be compressed is sucked into the cylinder bore from the suction chamber, and the suction medium is compressed in the cylinder bore and discharged into the discharge chamber.

In this compressor, the movement of the drive shaft in the axial direction is restricted by a thrust bearing that is screwed into the inner peripheral surface of one bearing hole and is held by the adjustment screw.
JP 2003-172417 A

  However, in the structure in which the thrust bearing is held by the adjustment screw in this way, after adjusting the axial position of the adjustment screw when screwing the adjustment screw, the screw groove of the adjustment screw or the screw in the bearing hole is used so that the adjustment screw does not loosen. It is necessary to restrict the axial movement of the adjusting screw by crushing the groove.

  Therefore, in the conventional structure, the assembly man-hour increases. Moreover, when crushing a screw groove, a fragment | piece may be produced and the stable operation | movement of a compressor may be inhibited.

  The present invention has been made paying attention to the problems of the prior art, and an object of the present invention is to provide a compressor having improved thrust bearing assembly.

  The present invention is a compressor, a bearing hole for supporting a drive shaft, and a thrust bearing for restricting movement of the drive shaft in the axial direction while being held in the bearing hole. A thrust bearing having a projecting piece projecting radially from the outer periphery thereof; and an insertion slit formed in the bearing hole for allowing the thrust bearing projecting piece to be inserted in an axial direction; and formed in the bearing hole. A thrust groove that receives the thrust bearing protrusion at a position displaced in the circumferential direction from the insertion slit and restricts the axial movement of the thrust bearing; and the thrust bearing protrusion is positioned in the stopper groove. An anti-rotation member that is inserted and locked in the insertion slit in a state where the thrust bearing is moved (rotated) in the circumferential direction. And butterflies.

  According to the present invention, the axial movement of the thrust bearing is restricted by the stopper groove, and the movement of the thrust bearing in the circumferential direction is restricted by the rotation preventing member. Thus, the axial movement of the drive shaft is restricted by the thrust bearing held in the bearing hole in a state where the movement in the axial direction and the rotational direction is restricted.

  Here, in the present invention, there is no step of adjusting the axial position of the adjuster screw by screwing the adjuster screw into the screw groove provided in the bearing hole as in the prior art, and after the adjuster screw is positioned, Since the process of crushing the thread groove or the thread groove of the bearing hole is not necessary, the process is simplified. In addition, since the caulking process of the thread groove is eliminated, the generation of fragments is eliminated, so that a stable operation of the compressor is ensured.

  Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings.

"Compressor"
First, the overall structure of the compressor will be described. FIG. 1 is an overall sectional view of the compressor.

  As shown in FIG. 1, the compressor 1 of the present embodiment is a variable capacity compressor, and has a plurality of cylinder bores 3 (in this example, five (see FIG. 5)) arranged at equal intervals in the circumferential direction. A cylinder block 2, a front head 4 joined to the front end surface of the cylinder block 2 and forming a crank chamber 5 between the cylinder block 2, and a suction end joined to the rear end surface of the cylinder block 2 via a valve plate 9. And a rear head 6 that forms a chamber 7 and a discharge chamber 8. The cylinder block 2, the front head 4, and the rear head 6 are fastened and fixed by a plurality of through bolts 13 to constitute a compressor housing.

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

  A suction valve mechanism for opening and closing the suction hole 11 is provided on the cylinder block 2 side of the valve plate 9, while a discharge valve mechanism (not shown) for opening and closing the discharge hole 12 is provided on the rear head 6 side of the valve plate 9. It has been. A gasket (not shown) is interposed between the valve plate 9 and the rear head 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained.

  A drive shaft 10 is pivotally supported through radial bearings 15 and 19 in central through holes 14 and 18 serving as bearing holes in the center of the cylinder block 2 and the front head 4, whereby the drive shaft 10 rotates in the crank chamber 5. It is free.

  A thrust bearing 20 is interposed between the front end surface of the rotor 21 fixed to the drive shaft 10 and the inner wall surface of the rear head 6. Further, a thrust bearing 16 is interposed between a coupler 17 as a rotation preventing member fixed to the central through hole 14 of the cylinder block 2 and the rear end surface of the drive shaft 10. These thrust bearings 16 and 20 restrict the movement of the drive shaft 10 in the axial direction. One thrust bearing 16 is constituted by a plate-like sliding bearing, and the other thrust bearing 20 is a pair of races, a plurality of needles as rolling elements held between the pair of races, and a pair of races. And a retainer that holds a plurality of needles in a freely rollable manner.

  A piston 29 is slidably accommodated in each cylinder bore 3.

  A conversion mechanism that converts the rotation of the drive shaft 10 into the reciprocating motion of the piston 29 is provided in the crank chamber 5. The conversion mechanism is connected to a rotor 21 as a rotating member fixed to the drive shaft 10, a sleeve 22 slidably mounted on the drive shaft 10 in the axial direction, and a pivot pin 23 connected to the sleeve 22. The swash plate 24 as a tilting member that can tilt with respect to the sleeve 22, and the rotor 21 and the swash plate 24 so that the rotational torque of the rotor 21 can be transmitted to the swash plate 24 while allowing a change in the tilt angle of the swash plate 24. A coupling mechanism 28 for coupling, and a pair of hemispherical piston shoes 30, 30 interposed between the swash plate 24 and the piston 29 for coupling the piston 29 to the outer periphery of the swash plate 24, are configured. Yes.

  The swash plate 24 is attached to the drive shaft 10 via a sleeve 22 and a pivot pin 23 so as to be tiltable with respect to the drive shaft 10 and slidable in the axial direction of the drive shaft 10. . In this example, the swash plate 24 includes a hub 25 in the center portion and a plate-like swash plate body 26 fixed to the boss portion 25 a of the hub 25.

  The inclination angle of the swash plate 24 decreases when the sleeve 22 moves closer to the cylinder block 2 against the return spring 52, while the inclination angle of the swash plate 24 decreases while the sleeve 22 resists the return spring 51. When moving in a direction away from 2, the inclination angle of the swash plate 24 increases.

  A drive transmission mechanism 40 is provided at one end of the drive shaft 10. The drive transmission mechanism 40 is rotatably attached to the outer periphery of the boss 4b of the front head 4 and is always rotated by an external drive source. The drive transmission mechanism 40 is fixed to the projecting end of the drive shaft 10 and rotates integrally with the drive shaft 10. Drive plate 42, and an electromagnetic clutch 43 that connects or disconnects the pulley 41 and the drive plate 42. The electromagnetic clutch 43 includes an electromagnetic solenoid 43 b fixed to the pulley 41 and a metal clutch plate 43 a fixed to the drive plate 42.

  When the electromagnetic clutch 43 is turned on to connect the pulley 41 and the drive plate 42, the drive shaft 10 rotates together with the pulley 41 that always rotates. When the drive shaft 10 rotates, the swash plate 24 rotates together with the rotor 21, and the piston 29 reciprocates at a stroke corresponding to the inclination angle of the swash plate 24. When the piston 29 reciprocates in this way, a medium to be compressed (for example, refrigerant) is sucked into the external circulation circuit → the suction chamber 7 → the suction hole 11 of the valve plate 9 → the cylinder bore 3 and is heated and heated in the cylinder bore 3. And is discharged from the cylinder bore 3 → the discharge hole 12 of the valve plate 9 → the discharge chamber 8 → the external circulation circuit.

  In order to change the discharge capacity of the refrigerant, the piston stroke is changed by changing the inclination angle of the swash plate 24. More specifically, by adjusting a differential pressure (pressure balance) between the crank chamber pressure Pc on the rear surface side of the piston 29 and the suction chamber pressure Ps on the front surface side of the piston 29, the inclination angle of the swash plate 24 is changed to change the piston. Change the stroke. Therefore, this variable capacity compressor is provided with a pressure control mechanism. The pressure control mechanism includes an extraction passage (not shown) that connects the crank chamber 5 and the suction chamber 7, an air supply passage (not shown) that connects the crank chamber 5 and the discharge chamber 8, and the air supply passage. And a control valve 33 that is provided in the middle of the air passage to control opening and closing of the air supply passage.

  When the air supply passage is opened by the control valve 33, high-pressure refrigerant gas flows from the discharge chamber 8 into the crank chamber 5 through the air supply passage, thereby increasing the pressure in the crank chamber 5. When the pressure in the crank chamber 5 increases, the sleeve 22 moves closer to the cylinder block 2 while the inclination angle of the swash plate 24 decreases, so that the piston stroke becomes smaller and the discharge amount decreases.

  On the other hand, when the air supply passage is closed by the control valve 33, the refrigerant gas has always escaped from the crank chamber 5 to the suction chamber 7 through the extraction passage, so that the pressure difference between the suction chamber 7 and the crank chamber 5 gradually disappears and becomes uniform. Pressure. Then, while the sleeve 22 moves away from the cylinder block 2, the inclination angle of the swash plate 24 increases, the piston stroke increases, and the discharge amount increases.

"Thrust bearing support structure"
Next, a support structure for a thrust bearing will be described with reference to FIGS.

  As described above, the thrust bearing 16 is constituted by a plate-like sliding bearing, and has a plurality of projecting pieces 16b that project in the radial direction from the outer periphery thereof. In this example, three protruding pieces 16b are provided at equal intervals in the circumferential direction. The thrust bearing 16 is locked in the bearing hole 14 by a coupler 17 as a rotation preventing member.

  An insertion slit 61 is formed in the bearing hole 14 to allow the protrusion 16b of the thrust bearing 16 to be inserted from the axial direction. The bearing hole 14 is provided with a stopper groove 63 that receives the protruding piece 16b of the thrust bearing 16 at a position displaced in the circumferential direction from the insertion slit 61 and restricts the axial movement of the thrust bearing 16. . The stopper groove 63 is provided over the entire circumference of the bearing hole 14 and is formed in an annular shape.

  The coupler 17 is inserted and locked in the insertion slit 61 in a state where the protruding piece 16 b of the thrust bearing 16 is positioned in the stopper groove 63, and restricts the rotation of the thrust bearing 16. The coupler 17 of the present embodiment includes a fitting portion 17b that is inserted and fitted into the insertion slit 61, and a connecting plate 17a that connects the plurality of fitting portions 17b. In this example, the connecting plate 17a is formed in a disc shape. The fitting portion 17b includes a protruding portion 17c that protrudes in a fan shape on the outer peripheral side of the connecting plate 17a, and a pair of opposing claw portions 17d that protrude in the axial direction from both circumferential ends of the protruding portion 17c. It is configured with. The claw portion 17d is formed in a square shape and bulges outward.

  Next, the assembly process of the thrust bearing 16 will be described with reference to FIGS.

  First, as shown in FIGS. 5 to 6, the thrust bearing 16 is inserted into the bearing hole 14 of the cylinder block 2. At this time, the thrust bearing 16 is inserted in a state where the protruding piece 16b of the thrust bearing 16 is aligned with the insertion slit 61 of the bearing hole 14.

  Next, as shown in FIGS. 6 to 7, the thrust bearing 16 is rotated in the circumferential direction so that the protruding piece 16 b of the thrust bearing 16 is displaced from the insertion slit 61 in the circumferential direction. Thereby, the protrusion 16b of the thrust bearing 16 enters the stopper groove 63, and the axial movement of the thrust bearing 16 is restricted.

  Next, as shown in FIGS. 7 to 8, the coupler 17 is inserted into the bearing hole 14, and the fitting portion 17 b of the coupler 17 is locked to the insertion slit 61. When the coupler 17 is inserted into the bearing hole 14, that is, when the fitting portion 17b of the coupler 17 is inserted into the insertion slit 61, the claw portion 17d of the fitting portion 17b is elastically deformed. Insertion into the insertion slit 61 is allowed, and the claw portion 17d is elastically restored at a predetermined position, whereby the claw portion 17d is caught at the boundary between the insertion slit 61 and the stopper groove 63, and the coupler 17 is directed in the direction opposite to the insertion direction. Is prevented from moving. That is, the coupler 17 is prevented from dropping from the insertion slit 61. When the coupler 17 is mounted, the thrust bearing 16 is prevented from rotating by the fitting portion 17b (mainly the pair of claw portions 17d in this example) of the coupler 17.

"effect"
The effects of this embodiment will be summarized below.

  (1) The compressor of this embodiment includes a bearing hole 14 for supporting the drive shaft 10 and a thrust bearing for restricting the movement of the drive shaft 10 in the axial direction while being held in the bearing hole 14. A thrust bearing 16 having a projecting piece 16b projecting radially from the outer periphery thereof, and an insertion slit 61 formed in the bearing hole 14 so that the thrust bearing projecting piece 16b can be inserted from the axial direction. The stopper groove 63, which is formed in the bearing hole 14 and receives the thrust bearing protrusion 16b at a position shifted in the circumferential direction from the insertion slit 14 and restricts the axial movement of the thrust bearing 16, and the stopper groove 63 An anti-rotation member that is inserted and locked in the insertion slit 61 in a state where the thrust bearing protrusion 16b is positioned, and restricts the rotation of the thrust bearing 16 It includes a 7, a.

  Therefore, unlike the conventional structure using an adjuster screw, after adjusting the axial position of the adjuster screw by screwing the adjuster screw into the screw groove provided in the bearing hole, the screw groove or bearing hole of the adjuster screw is adjusted. This eliminates the need for crushing the screw groove and simplifies the thrust bearing assembly process. In addition, since it is not necessary to caulk the thread groove, the generation of fragments is eliminated, so that a stable operation of the compressor is ensured.

  (2) In the compressor of the present embodiment, the thrust bearing 16 is a plate-like sliding bearing. Therefore, the structure is further simplified, and the assembly process of the thrust bearing 16 is simplified.

  (3) In the compressor of the present embodiment, the thrust bearing 16 is held in the bearing hole 14 on the opposite side to the side that receives the compression reaction force of the piston 29 out of the pair of bearing holes 14 and 18. Therefore, since it is difficult for a large force to be applied to the thrust bearing 16 via the drive shaft 10, even if the thrust bearing 16 is configured by a plate-like slide bearing, it can be configured with a simple structure without providing any other stopper mechanism. .

  The present invention is not limited to the embodiment described above.

  In the above-described embodiment, a swash swash plate (rotary swash plate) is used. However, in the present invention, a wobble swash plate (non-rotating swash plate) may be used. Alternatively, a swash plate may be used.

  Various other modifications are possible as long as they belong to the technical scope of the present invention.

FIG. 1 is a cross-sectional view of a compressor according to an embodiment of the present invention. FIG. 2 is a perspective view showing the entire cylinder block in phantom lines to show the internal structure of the bearing hole of the cylinder block of the compressor. 3 is an exploded perspective view of FIG. FIG. 4 is a perspective view of the coupler 17 of the compressor. FIG. 5 is a view showing a state before the thrust bearing and the coupler are inserted in order to explain the assembly process of the thrust bearing of the compressor, where (a) is a rear end view of the cylinder block, and (b) is ( The BB sectional drawing in a), (c) is CC sectional drawing in (a). 6A and 6B are views showing a state after the thrust bearing is inserted in order to explain the assembly process of the thrust bearing of the compressor, wherein FIG. 6A is a rear end view of the cylinder block, and FIG. BB sectional drawing of (b), (c) is CC sectional drawing in (a). FIG. 7 is a view showing a state in which the thrust bearing is rotated after the thrust bearing has been inserted in order to explain the assembly process of the thrust bearing of the compressor, wherein (a) is a rear end view of the cylinder block; ) Is a BB sectional view in (a), and (c) is a CC sectional view in (a). FIG. 8 is a view showing a state after the coupler is inserted in order to explain the assembly process of the thrust bearing of the compressor, where (a) is a rear end view of the cylinder block and (b) is a view in (a). BB sectional drawing of (b), (c) is CC sectional drawing in (a).

Explanation of symbols

1 ... Variable capacity compressor 2 ... Cylinder block (housing)
3 ... Cylinder bore 4 ... Front head (housing)
5 ... Crank chamber 6 ... Rear head (housing)
7 ... Suction chamber 8 ... Discharge chamber 10 ... Drive shaft 14 ... Central through hole (bearing hole)
DESCRIPTION OF SYMBOLS 16 ... Thrust bearing 16b ... Projection piece 17 ... Coupler 17a ... Connecting plate 17b ... Fitting part 17c ... Projection part 17d ... Claw part 61 ... Insertion slit 63 ... Stopper groove

Claims (3)

A bearing hole (14) for pivotally supporting the drive shaft (10);
A thrust bearing (16) for restricting movement of the drive shaft (10) in the axial direction while being held in the bearing hole (14), and a projecting piece projecting radially from the outer periphery thereof A thrust bearing (16) having (16b);
An insertion slit (61) formed in the bearing hole (14) and allowing the thrust bearing protrusion (16b) to be inserted from an axial direction;
The thrust bearing (16) is moved in the axial direction by receiving the thrust bearing protrusion (16b) at a position formed in the bearing hole (14) and shifted in the circumferential direction from the insertion slit (14). A stopper groove (63) to be regulated;
A rotation-preventing member (17) that is inserted and locked in the insertion slit (61) in a state in which the thrust bearing protrusion (16b) is positioned in the stopper groove (63) and restricts the rotation of the thrust bearing (16). )When,
A compressor comprising: The cylinder bore (3), the suction chamber (7), the discharge chamber (8), the crank chamber (5), and a pair of bearing holes (14) provided on both sides of the crank chamber across the crank chamber (5). 18) and a housing (2, 4, 6) having an inside thereof,
A drive shaft (10) pivotally supported in the pair of bearing holes (14, 18) via bearings and rotatably disposed in the crank chamber (5);
A piston (29) that reciprocates within the cylinder bore (3) in conjunction with rotation of the drive shaft (10);
With
A compressor that sucks and compresses fluid from the suction chamber (7) into the cylinder bore (3) by reciprocating movement of the piston (29), and compresses the compressed fluid into the discharge chamber (7).
A thrust bearing (16), which is held in one bearing hole (14) of the pair of bearing holes (14, 18) and restricts movement of the drive shaft (10) in the axial direction. A thrust bearing (16) having a projecting piece (16b) projecting in the direction;
An insertion slit (61) provided in the one bearing hole (14) and extending in the axial direction to allow the thrust bearing protrusion (16b) to be inserted from the axial direction;
A stopper groove (63) provided in the one bearing hole (14) and extending in a circumferential direction from the insertion slit (61) so as to communicate with the insertion slit (61), the thrust bearing A stopper groove (63) for restricting axial movement of the thrust bearing (16) in a state where the protruding piece (16b) is located in the stopper groove (63),
An anti-rotation member that restricts rotation of the thrust bearing (16) by being inserted and locked in the insertion slit (61) in a state where the thrust bearing protrusion (16b) is positioned in the stopper groove (63). (17) and
A compressor comprising: The compressor according to claim 1 or 2,
The compressor according to claim 1, wherein the thrust bearing (16) is a plate-like sliding bearing.

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