KR100202791B1 - Variable capacity compressor - Google Patents

Abstract

An object of the present invention is to secure smooth movement of a swash plate and to provide a swash plate type compressor in which a hinge mechanism K is provided with an arm 15 protruding from the top of the swash plate 11, The arm 15 is formed so that a columnar surface 16a having a convex curved surface extends in a direction perpendicular to the inclined axis of the swash plate 11 And the coupling groove 17 slidably contacts the column surface 16a of the arm head portion 16 and is engaged with the piston 16 so that the piston 16 is slidably in contact with the piston 16, A guide wall 17a for holding the top dead center position of the arm head portion 9 as constant as possible and a protruding frame portion 17b for supporting both end faces of the arm head portion 16 with the guide wall 17a therebetween The smooth displacement of the swash plate is ensured with a simple configuration.

Description

Variable capacity compressor

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a refrigerant compressor, and more particularly to a variable displacement compressor equipped with a short-headed piston.

A wobble type swash-type variable displacement compressor mainly provided for vehicle air control has a configuration in which a swash plate connected through a rotor and a hinge mechanism can be inclined around support points, and a crank chamber pressure , The force acting on the back surface of the single-headed piston is controlled and the inclined displacement in the direction of the supporting point of the swash plate, that is, the piston stroke is variably controlled by the balance of the force and the gas pressure acting on the front surface of the piston .

The hinge mechanism that simultaneously receives the torque transmission to the swash plate and the guide for the inclined angle displacement is disclosed in, for example, Japanese Patent Application Laid-Open No. 6-264865, as disclosed in a number of publications, And the swash plate is rotatably connected to the rotor by passing the pivot pin through the elongated hole on the other side of the rotor or swash plate.

However, in the hinge mechanism described above, in addition to the processing of long holes, the number of parts such as pivot pins and stop rings is large, and productivity is improved. In addition, as disclosed in the above publication, In the configuration in which the connecting portions of the swash plates forming the holes are arranged in parallel in the axial direction of the pins, the thrust load acting on the swash plate due to the gas compression acts as a bending moment on the pin of one support shape, So that the point of force of the pin also inevitably changes in point contact.

Therefore, in such a compressor, there is a problem that abnormal wear tends to proceed in the hinge mechanism for guiding the inclination angle displacement of the swash plate during the continuation of the high-speed or high compression ratio operation. Furthermore, in the structure in which the swash plate is mounted on the main shaft through the center hole as in the compressor of the present invention, a point contact slide with the main shaft due to the inclination of the swash plate is formed at the end edge portions of the center hole at the inclination angle of the swash plate , And if this is repeated over a long period of time, the progress of wear of both sides can be a cause of damaging the accurate and smooth inclination angle displacement of the swash plate. In addition, in the compressor, the bush is covered with the pivot pin, and a part of the peripheral surface of the bush is brought into surface contact with the wall surface of the long hole. However, the fundamental disadvantage based on the inclination of the swash plate Still not resolved.

An object of the present invention is to solve the problem of ensuring a smooth displacement operation of the swash plate with a simple structure.

FIG. 1 is a cross-sectional view showing an entire configuration of a compressor according to an embodiment of the present invention; FIG.

Fig. 2 is a front view showing a hinge mechanism of the compressor. Fig.

FIG. 3 is a plan view showing a hinge mechanism of the compressor. FIG.

FIG. 4 is a plan view showing another embodiment of the hinge mechanism. FIG.

FIG. 5 is an enlarged front view showing the mooring means of the hinge mechanism; FIG.

FIG. 6 is a cross-sectional view taken along the line A-A of FIG. 4 showing the mooring means of the hinge mechanism;

FIG. 7 is a sectional view similar to FIG. 6 showing a modified example of the copper flow means. FIG.

Fig. 8 is an enlarged sectional view showing a through hole of the swash plate in the compressor. Fig.

DESCRIPTION OF THE REFERENCE NUMERALS

1: Cylinder block 2: Front housing

3: rear housing 5: crank chamber

6: drive shaft 8: cylinder bore

9: piston 10: rotor

11: inclined plate 15: arm

16: head portion 16a:

17: engaging groove 17a: guide wall

17b: protruding rim 20: through hole

20a: Support part 43: Sphere

44: raceway groove K: hinge mechanism

(1) According to a first aspect of the present invention, there is provided a compressor comprising: a cylinder block having a plurality of bores arranged in parallel to constitute an outer periphery of a compressor; a front housing closing a front end of the cylinder block by forming a crank chamber therein; A rear housing having a suction chamber and a discharge chamber and closing the rear end of the cylinder block, a swash plate connected to the rotor moving together with the drive shaft via a hinge mechanism so as to be synchronously rotatable, The hinge mechanism includes at least an arm including a load region of the swash plate and protruding from the front surface of the swash plate, and an arm disposed in the same phase And an engaging groove formed in the rotor for supporting the arm with a convex curved surface A guide wall slidably contacting the column surface of the arm head to keep the top dead center position of the piston as unchanged as possible; And a protruding edge for supporting both end portions of the arm head portion with the guide wall therebetween.

In other words, since the hinge mechanism includes only the arm projected from the swash plate and the engaging groove formed in the rotor, the structure is extremely simplified, and in addition, the hinge mechanism has a columnar surface of the arm head, And both end faces are stably received by the guide wall and the protruding rim of the engaging groove. It is also possible to reduce the contact surface pressure between both of the column surfaces of the arm head and the engagement grooves by appropriately selecting the shapes of both of the guide walls of the arm head while keeping the top dead center position of the piston substantially unchanged.

(2) The compressor according to claim 2 is characterized in that, in the compressor according to claim 1, the arm head portion is formed to be laterally symmetrical beyond the top dead center position of the swash plate.

That is, the head of the arm formed in the left-right symmetry is not effective to maintain the balance of the swash plate, and even if the driving system is set in the rotational direction of the left-right shift, there is an advantage of reacting immediately.

(3) The compressor according to Claim 3 is characterized in that, in the compressor according to Claim 1, the arm head portion is formed so as to be closer to the compression discharge side than the top dead center position of the swash plate.

That is, the head portion of the arm mainly covers the action region of the compressive load, thereby suppressing the enlargement of the arm itself and contributing to weight reduction of the airframe.

(4) The compressor according to claim 4 is characterized in that, in the compressor according to claim 1, 2 or 3, the arm head has a width sufficient to accommodate a high action area of the compression load.

That is, the entire width of the columnar surface that embraces the ancient action area of the compression load is reliably received in accordance with the guide wall and the protruding rim of the engaging groove. As a result, even when the dynamic load acting point transitions to the swash plate, .

(5) The compressor according to claim 5 is characterized in that, in the compressor according to claim 1, 2, 3 or 4, the convex curved surface forming the columnar surface of the arm head is an arc surface.

That is, if such an arc surface is employed, the formation of the column surface is simplified to one layer, which is considerably advantageous from the viewpoint of productivity.

(6) The compressor according to claim 6 is characterized in that, in the compressor according to any one of the first to fifth aspects, a shoe is mounted between the column surface of the arm head and the guide wall of the coupling groove.

That is, by the intervention of the shoe, the contact form of the hinge mechanism is converted into surface contact, and the progress of the abrasion can be reasonably suppressed.

(7) The compressor according to claim 7 is characterized in that in the compressor according to any one of claims 1 to 6, a mooring means for preventing the arm head from departing is disposed between the arm head and the protruding rim of the coupling head .

That is, when the load acting on the swash plate is canceled, such as when the compressor is stopped, the gutter attachment due to the floating of the arm head and the fall of the shoe can be reliably prevented.

(8) In the compressor according to claim 8, in the compressor according to claim 7, the mooring means comprises an orbit groove formed in the protruding rim and an engaging member embedded in the arm head and fitted in the orbit groove .

That is, by doing so, it is possible to reliably prevent the flow from dropping out while maintaining the simple configuration and accurate and smooth operation of the arm by the arm.

(9) A compressor as set forth in claim 9, comprising: a cylinder block having a plurality of bores arranged in parallel to constitute an outer periphery of the compressor; a front housing closing a front end of the cylinder block by forming a crank chamber therein; A rear housing which has a suction chamber and a discharge chamber and which closes a rear end portion of the cylinder block and a rotor which moves together with the drive shaft and which is rotatably connected via a hinge mechanism so as to be synchronously rotatable, The hinge mechanism including a swash plate guided by the drive shaft engaged with the through hole formed in a hole shape and capable of being inclined at an angle over the entire control range, and a piston linearly moving in the bore in association with the swash plate, An arm including a load acting region of the swash plate and protruding from the front surface thereof; And a coupling groove formed by the rotor for supporting the arm in the same phase, wherein the arm has a curved surface having a convex curved surface extending in a direction orthogonal to the tilted axis of the tilted plate, And a protruding edge for supporting both end portions of the arm head portion with the guide wall therebetween.

That is, in the compressor in which the through hole of the swash plate is provided in the drive shaft and the support portion formed in the through hole is directly or indirectly slidably in contact with the drive shaft, in the compressor in which the inclined plate displacement posture is regulated, The hinge mechanism is more advantageous.

The swash plate is a swash plate that can be used for either a wobble type in which the swash plate combined with the swash plate is connected to the piston through the con rod and a swash type in which the swash plate is directly connected to the piston through the shoe, The plane (raceway surface) is a plane sharing the upper and lower dead points of the swash plate and the drive shaft.

BRIEF DESCRIPTION OF THE DRAWINGS Fig.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings.

1 to 3, the front housing 2 is joined to the front end side of the cylinder block 1, and the rear housing 3 is connected to the rear end side through the valve plate 34. As shown in Fig. A drive shaft 6 extending in the axial direction is accommodated in a crank chamber 5 formed by the cylinder block 1 and the front housing 2. The drive shaft 6 is rotatably supported by bearings 7a and 7b, Are supported. A plurality of cylinder bores 8 are perforated around the drive shaft 6 in the cylinder block 1 and a piston 9 is provided in each cylinder bore 8.

A rotor 10 is fixedly attached to the drive shaft 6 in the crank chamber 5 and supported by bearings 19 between the rotor 10 and the front housing 2. A through hole 20, the swash plate 11 is provided.

The through hole 20 is formed so as to extend over the entire control range about the pivot axis Y that is set beyond the movement axis 6 on the side opposite to the hinge mechanism K described later with the drive shaft shim therebetween. 6, the position of the swash plate 11 in the radial direction, in particular, the swash plate 11 (i.e., the swash plate 11) The support portion 20a for regulating the radial position in the plane (inclined raceway surface) sharing the drive shaft paddle S with the upper and lower dead points of the pivot shaft 11 is formed in an arcuate shape about the pivot Y, The inner surface 20b on the side of the minimum inclination angle of 10 to 15 The allowable inclination angle of ₁ ). On the inner diameter surface 20c on the maximum inclination angle side, a clearance angle of 1 to 2 ^degrees ( ₂ ). On both sides of the through hole 20, a flat regulating surface 20d is formed in association with the formation of a bent long hole.

1, a coil spring 12 for applying a backward force to the swash plate 11 is mounted between the rotor 10 and the swash plate 11. On the other hand, on the outer periphery of the swash plate 11, And the hemispherical portion of the furrows 14 and 14 is engaged with the spherical support surface of the piston 9 so that a plurality of The piston 9 of each cylinder bore 8 is reciprocably housed.

1, a coil spring 12 for pushing the swash plate 11 backward is mounted between the rotor 10 and the swash plate 11. On the other hand, on the outer peripheral portion of the swash plate 11, And the hemispherical portions of the shoe 14 and 14 are engaged with the spherical support surface of the piston 9 so that the plurality of pistons 9 moored to the swash plate 11 are engaged And is accommodated so as to reciprocate within the cylinder bore 8.

The suction port 32 and the discharge port 33 are formed in the valve plate 4 so as to correspond to the cylinder bore 8 and are formed in the rear housing 3 in the suction chamber 30 and the discharge chamber 31, And a compression chamber formed between the valve plate 4 and the piston 9 is connected to the suction chamber 30 and the discharge chamber 31 through the suction port 32 and the discharge port 33. [ Each suction port 32 is provided with a suction valve that opens and closes the suction port 32 in accordance with the reciprocating motion of the piston 9 and a discharge port 33 which is connected to the discharge port 33 in accordance with the reciprocating motion of the piston 9 And a discharge valve (not shown) for opening and closing while being restricted by the retainer 34 are provided. A non-illustrated control valve for adjusting the pressure of the crank chamber 5 is mounted on the rear housing 3.

The hinge mechanism which is most characteristic of the present invention will now be described in detail with reference to FIGS. 2 and 3.

The arm 15 constituting the hinge mechanism K is symmetrically arranged beyond the position of the top dead center P shown in FIG. 3 and the upper rear surface of the rotor 10 A coupling groove 17 for supporting the arm 15 in the same phase is formed. As shown in the drawing, the arm 15 has a columnar surface 16a having a convex curved surface extending in a direction orthogonal to the tilted axis of the swash plate 11 and capable of embracing the ancient action area T of the compressive load And the coupling groove 17 is parallel to the column surface 16a and inclined rearward toward the axis and is in sliding contact with the column surface 16a, A projection wall 17a for holding the top dead center position of the piston 9 as constant as possible and a projection frame 17b for supporting both end faces of the arm head portion 16 with the guide wall 17a therebetween Respectively.

When the swash plate 11 moving together with the drive shaft 6 is rotated in accordance with the start of the compressor constructed as described above, the pistons 9 reciprocate in the cylinder bores 8 through the shoe 14, 14 , Whereby the refrigerant gas is sucked from the suction chamber (30) to the compression chamber, and the refrigerant is compressed and discharged to the discharge chamber (31). At this time, the discharge capacity of the refrigerant gas discharged into the discharge chamber (31) is controlled by adjusting the pressure in the crank chamber (5) by the control valve.

That is, when the pressure of the crank chamber 5 rises due to the pressure adjustment of the control valve in the state of FIG. 1, the inclination angle of the swash plate 11 is reduced by increasing the back pressure acting on the piston 9. The head portion 16 of the arm 15 constituting the hinge mechanism K rotates in the counterclockwise direction and the columnar surface 16a of the arm portion 15 of the arm 15 constituting the hinge mechanism K is moved outward along the guide wall 17a of the engaging groove 17 And at the same time the swash plate 11 is pushed by the coil spring 12 and moves backward while the support portion 20 of the arc shape about the pivot Y is kept in collision contact with the drive shaft 6 . As a result, the inclination angle of the swash plate 11 is reduced, and the discharge capacity is reduced at the same time as the stroke of the piston 9. The minimum capacity is set such that the spot filling surface 11b formed at the rear end of the through hole 20, (13).

Conversely, when the pressure in the crank chamber 5 is lowered by the pressure adjustment of the control valve in such a state that the discharge capacity is small, the inclination angle of the swash plate 11 is increased by lowering the back pressure acting on the piston 9. The head 16 of the arm 15 is rotated in the clockwise direction and slides inward along the guide wall 17a of the columnar surface 16a in the spacing direction with respect to the axial center while the swash plate 11 is supported by the support portion 20a move forward against the coil spring 12 while maintaining contact with the drive shaft 6. [ As a result, the inclination angle of the swash plate 11 is enlarged, and the discharge capacity increases simultaneously with the stroke of the piston 9. The maximum capacity of the swash plate 11 is determined by the impact engagement surface 11a projected on the front surface of the swash plate 11, (10a) of the base (10).

In this case, since only the arm 15 protruding from the swash plate 11 and the coupling groove 17 formed with the rotor 10 are used as the main parts, the hinge mechanism K has a very simple structure, The entire width of the columnar surface 16a accommodating the action region T of the compressive load is reliably received by the guide wall 17a and the protruding edge 17b of the engaging groove 17, The inclination of the swash plate 11 due to the warping does not occur at all. Further, since the arm 15 integrated with the swash plate 11 is inevitably formed of an aluminum alloy or the like, it can contribute to weight reduction compared with the conventional hinge mechanism using an iron-based material such as a pivot pin. In addition, since the curvature radius of the convex curved surface forming the columnar surface 16a can be set to be extremely large as compared with the conventional pivot fin, the pressure on the contact surface with the guide wall 17a can be easily reduced.

The convex curved surface forming the columnar surface 16a may be formed as a circular arc surface and the guide wall 17a slidably contacting with the convex curved surface may be formed as a flat surface. ), Or to further reduce the contact surface pressure of both of them.

As shown in Fig. 1, in the compressor having the swash plate 11 guided by the drive shaft 6 engaged with the through hole 20 formed in a bent long hole shape and capable of inclining at an inclination angle over the entire control range, The hinge mechanism K is further advantageous because it is difficult to support the moment acting on the swash plate 11 between the hinge mechanism 6 and the hinge mechanism 6. [

The embodiment of the hinge region K shown in Fig. 1 is obtained by mounting a shoe 18 which has a convex curved surface forming the columnar surface 11 as a circular arc surface and which is tightly coupled with both of the guide walls 17a In this way, the machining of the columnar surface 16a can be simplified and the mutual contact form can be converted into surface contact, which is remarkably effective for reducing wear.

The arm 115 according to the other embodiment shown in Fig. 4 is provided so as to protrude from the position of top dead center P of the swash plate 111 in the compression discharge side (preceding rotational side) On the upper rear side, a coupling groove 117 for supporting the arm 115 in phase is formed. The arm 115 is formed so that a columnar surface 116 formed of a convex curved surface extends in a direction orthogonal to the area raceway surface of the swash plate 111 and has a width sufficient to accommodate the anticipated area T of compressive load And has a head portion 116. The remaining configuration is completely the same as the previous embodiment.

Therefore, the arm head 116 in the present embodiment substantially covers the action area of the compression load, more preferably the entire area of the ancient action area T, which is unevenly distributed to the side of the compression plate of the swash plate 111, It is possible to contribute to the weight reduction of the airframe.

5 and 6 show the mooring means provided between the arm head 16 and the protruding rim 17b of the coupling groove 17 and the load acting on the swash plate 11 The swinging of the arm head 16 and the removal of the shoe 18 are prevented by the floating motion of the arm head 16.

That is, at the center of the convex curved surface of the arm head portion 16, the small holes 41 are provided in the extending direction of the column surface 16a, the pins 42 as the engaging members are inserted into the small holes 41, (43), which resembles the movement locus of the small hole (41), is provided on the inner surface of at least one side of the small hole (17b). The engagement of the protruding end of the pin 42 with the raceway groove 43 prevents the movement of the arm 15 relative to the engaging groove 17 without interfering with the smooth operation of the arm 15. [ Is completely prevented.

7 shows a modified example of the mooring means. A small hole 41A is formed in the center of the convex curved surface of the arm head 16 in the extending direction of the columnar surface 16a, (Engaging member) 42A capable of protruding and retreating due to the pushing force of the screw 44 is disposed on the inner surface of the protruded rim 17b while a semicircular section The raceway grooves 43A of the raceway are engraved. Accordingly, this form also prevents the flow-off of the arm 15 relative to the engaging groove 17.

INDUSTRIAL APPLICABILITY As described above, the compressor according to the present invention has the structure described in the claims, and therefore has the following excellent effects.

(1) Since the swing plate is smoothly displaced by the simple structure of the hinge mechanism, and even when the point of action of the load acting on the swash plate is shifted, there is no inclination of the swash plate due to the twist. It is possible to effectively prevent uneven wear of the swash plate and the drive shaft.

(2) Since the contact surface pressure of the relative sliding surface of the hinge mechanism can be reduced, it is very effective in preventing wear of both sliding surfaces.

(3) Since the mooring means is provided between the arm constituting the hinge mechanism and the engaging groove, the anxiety of the flow disengagement of the arm is completely eliminated.

Claims (9)

A front housing for closing the front end of the cylinder block by forming a crank chamber therein; a drive shaft rotatably supported by the cylinder block and the front housing; A rear housing having a suction chamber and a discharge chamber for closing the rear end of the cylinder block; a swash plate connected to the rotor moving together with the drive shaft through a hinge mechanism so as to be synchronously rotatable; Wherein the hinge mechanism includes at least an arm including a load region of the swash plate and projecting to a front surface thereof, and a coupling formed on the rotor for supporting the arm in the same phase, Wherein the arm has a convex curved surface, Wherein the engaging groove has a guide wall slidably abutting against the column surface of the arm head so as to keep the top dead center position of the piston as unchanged as possible, And a protruding edge for supporting both end portions of the arm head portion. The variable displacement compressor according to claim 1, wherein the arm head is formed symmetrically beyond the top dead center position of the swash plate. 2. The variable capacity compressor according to claim 1, wherein the arm head is formed so as to be closer to the compression discharge side than the position of the top dead center of the swash plate. The variable displacement compressor according to claim 1, 2, or 3, wherein the arm head has a width sufficient to accommodate the anticipated area of the compression load. The variable capacity compressor according to claim 1, 2 or 3, wherein the convex curved surface forming the columnar surface of the arm head is an arc surface. The variable displacement compressor according to claim 1, 2, or 3, wherein a shoe is mounted between the columnar surface of the arm head and the guide wall of the coupling groove. The variable displacement compressor according to claim 1, 2, or 3, wherein a mooring means is disposed between the arm head and the protruding rim of the coupling head to prevent the arm head from departing. 8. The variable capacity compressor according to claim 7, wherein the mooring means comprises an orbit groove formed in the protruding rim and an engaging member embedded in the arm head and fitted in the orbit groove. A front housing for closing the front end of the cylinder block by forming a crank chamber therein; a drive shaft rotatably supported by the cylinder block and the front housing; A rear housing which has a suction chamber and a discharge chamber and closes a rear end portion of the cylinder block, and a through hole formed in a curved long hole shape so as to be synchronously rotatable through a hinge mechanism to a rotor moving together with the drive shaft Wherein the hinge mechanism comprises: a swash plate that is guided by the drive shaft to be displaced at an inclination angle over the entire control range; and a piston that linearly moves in the bore in association with the swash plate, An arm protruding into the front surface thereof, Wherein the arm has a head portion having a convexly curved surface and extending in a direction perpendicular to the tilted axis of the tilting plate, wherein the engaging groove slidably contacts with a columnar surface of the arm head portion, A guide wall for keeping the top dead center substantially unchanged, and a protruding frame for supporting both end portions of the arm head portion with the guide wall interposed therebetween.