KR20060096379A - Swash plate type variable displacement compressor - Google Patents

Abstract

The variable displacement swash plate compressor has a housing, a drive shaft, a piston, a lug plate, a swash plate, a hinge mechanism provided between the lug plate and the swash plate, and a control mechanism. The hinge mechanism is located on the suction side with respect to the first virtual plane including the top position of the swash plate corresponding to the top dead center position of the piston and the axis of the drive shaft, constrains the relative rotation of the lug plate and the swash plate, and at the same time the swash plate lugs And a restraining hinge that restrains movement in a direction away from the plate. The hinge mechanism further includes an unconstrained hinge that is located on the discharge side with respect to the first virtual plane and does not restrict the swash plate from moving in a direction away from the lug plate.

Description

Capacity variable swash plate compressor {SWASH PLATE TYPE VARIABLE DISPLACEMENT COMPRESSOR}

1 is a longitudinal sectional view of a variable displacement swash plate compressor according to a preferred embodiment of the present invention.

2 is a partially enlarged cross-sectional view of a compressor according to a preferred embodiment of the present invention as seen from the rear side of FIG.

3 is a front view of a swash plate according to a preferred embodiment of the present invention.

4 is a bottom view of a swash plate according to a preferred embodiment of the present invention.

5 is a partially enlarged cross-sectional view of a compressor according to a preferred embodiment of the present invention in which the inclination of the swash plate indicates the minimum inclination angle.

6 is a partially enlarged cross-sectional view of a compressor according to a preferred embodiment of the present invention as seen from the rear side of FIG. 5, wherein the inclination of the swash plate represents the minimum inclination angle.

7 is a schematic front view of a swash plate, hinge mechanism and lug plate according to a preferred embodiment of the present invention showing the relationship between the lug plate and the swash plate.

<Explanation of symbols for main parts of drawing>

1 housing 4 control mechanism

10: variable displacement swash plate compressor

11: cylinder block 11a: cylinder bore

12: front housing 13: rear housing

15: crank chamber l6: drive shaft

22: extending hole 23: faces facing in parallel

24: lug plate 25: swash plate

25a: receiving surface 25b: weight

26 hinge mechanism 31 piston

32: shoe 33: compression chamber

34: discharge chamber 35: suction chamber

44: supply passage 45: bleed passage

46: capacity control valve 60: restraint hinge

61 support arm 61a guide hole

62: guide pin 62a: spherical portion

70: unbound hinge 71: first guide surface

72: second guide surface

A: top position 01: axis

CP: first virtual plane SP: second virtual plane

The present invention relates to a variable displacement swash plate compressor.

Japanese Laid-Open Patent Publication No. Hei 9-203377 discloses a conventional variable displacement swash plate type compressor (hereinafter only referred to as "compressor"). The compressor is internally formed with a cylinder bore, a crank chamber, a suction chamber and a discharge chamber, a piston reciprocally housed within the cylinder bore to partition the compression chamber, and driven by an external drive source to be rotatable in the housing. It is provided with a drive shaft supported. In addition, the compressor has a lug plate supported synchronously with the drive shaft in the crank chamber, and a swash plate for synchronously rotating and tilting the drive shaft through the lug plate and the hinge mechanism to reciprocate the piston through the shoe. Doing. In the center of the swash plate, a drawing hole is formed which is inserted into the drive shaft and accommodated by a surface facing the outer circumferential surface of the drive shaft in parallel. Moreover, this compressor is equipped with the control mechanism which controls the pressure in a crank chamber.

The hinge mechanism of this compressor is located in close proximity on an imaginary plane including the top position of the swash plate corresponding to the top dead center position of the piston, the top position of the drive shaft and the axis, and does not restrain the swash plate from moving away from the lug plate. It includes an arm as a hinge element and an engagement groove. An arm is formed in the swash plate and has a first guide surface facing toward the lug plate. The engagement groove is formed in the lug plate and has a second guide surface which can contact the first guide surface facing toward the swash plate side. In this non-binding hinge, the top end of the arm is held in the engagement groove, thereby restraining the relative rotation of the lug plate and the swash plate.

The compressor described above constitutes a refrigeration circuit of an automobile together with a condenser, an expansion valve, an evaporator, and the like. When the swash plate rotates at an inclined angle in accordance with the drive of the drive shaft by an engine or the like as an external drive source, the piston reciprocates in the cylinder bore. Therefore, the refrigerant gas is sucked from the suction chamber into the compression chamber in the cylinder bore, compressed, and discharged to the discharge chamber. The control mechanism adjusts the pressure in the crank chamber to change the inclination angle of the swash plate, whereby the discharge capacity of the refrigerant gas discharged from the pressure chamber to the discharge chamber is controlled. Therefore, the cooling capacity according to the discharge capacity of the refrigerating circuit is realized by the refrigerating circuit.

During operation of the compressor, the compression reaction force and the suction force of the refrigerant gas are applied to the swash plate through the piston and the shoe, thereby acting on the swash plate to incline with respect to the drive shaft to rotate around the intersection between the swash plate and the virtual plane. In a non-constrained hinge element in which the uppermost end of the arm is held in the engagement groove, both sides of the arm contact the inner wall of the engagement groove to receive the moment. A drawing hole formed in the center of the swash plate receives this moment on its parallel facing surface.

In addition, Japanese Patent Laid-Open No. 2917767 discloses a compressor having a hinge mechanism different from the hinge mechanism having the above-described configuration. In this compressor, the hinge mechanism is located on the suction side and the discharge side with respect to the imaginary plane, instead of the arm and the engaging groove as the above-mentioned non-binding hinge, restraining the relative rotation between the lug plate and the swash plate, and the swash plate It consists of a pair of restraining hinges which restrain the movement in the direction away from this lug plate. Each restraining hinge is formed of a lug plate, a support arm having a guide hole, and a guide pin having a spherical portion formed in the swash plate and sliding in the guide hole.

In the compressor of Japanese Patent No. 2917767 described above, the pressure in the crankcase is adjusted by a control mechanism, as in the compressor of Japanese Patent Application Laid-open No. Hei 9-203377, and the inclination angle of the swash plate is changed, thereby discharging from the compressor. The discharge capacity of the refrigerant gas discharged to the chamber is controlled.

During operation of the compressor, a pair of restraining hinges rotate about the intersection of the swash plate and the imaginary plane to accommodate the moment of inclination with respect to the drive shaft. In addition, the moment in which the drawing holes formed in the center of the swash plate face in parallel are also accommodated.

However, in the compressor, there is a concern that the following problems may occur regarding the reduction of vibration and noise during operation of the compressor.

In the compressor of Japanese Patent Application Laid-Open No. 9-203377, when the compressor is operated at high speed and high capacity while the refrigerant gas is insufficient in the refrigeration circuit, the large stroke of the piston is also reciprocated at high speed. This does not increase the discharge pressure to the desired value. Therefore, the inertial force of the piston tends to be larger than the compression reaction force, whereby the moment to increase the inclination angle of the swash plate acts on the swash plate. The hinge mechanism of the compressor of Japanese Unexamined Patent Publication No. 9-203377, which is a non-restraining hinge element that does not restrain the swash plate from moving in a direction away from the lug plate, is generated by the excessive inertia force of the piston to further incline the swash plate. Do not accept the moment to increase. Therefore, there is a fear that the inclination angle of the swash plate may incline beyond the maximum inclination angle. In this case, there is a possibility that a problem occurs that the piston reciprocates at a distance longer than the maximum stroke, and the piston head collides against the suction valve of the uppermost wall in the compression chamber, causing abnormal vibration or noise.

In the compressor of Japanese Patent Publication No. 2917767, since the hinge mechanism is a pair of restraining hinge elements that restrain the swash plate from moving in a direction away from the lug plate, the hinge mechanism is generated by the excessive inertia force of the piston to further extend the swash plate. It can accept moments that can be tilted. Therefore, the swash plate does not incline beyond the maximum inclination angle, and occurrence of abnormal vibration and noise due to excess inclination of the swash plate exceeding the maximum inclination angle is prevented.

However, in the compressor of Japanese Patent No. 2917767, each of the restraining hinge elements restrains the relative rotation between the lug plate and the swash plate, and restrains the swash plate from moving in a direction away from the lug plate, thereby smoothing the hinge mechanism. In order to realize one operation, the clearance of each constraint hinge needs to be increased appropriately. This is because reducing the clearance of the constrained hinge elements and at the same time increasing the positioning precision of each constrained hinge element of the mass produced compressor is limited in terms of manufacturing cost and productivity. Due to the large clearance of the restraining hinge element, it may cause a gap between the swash plate and the shoe, and also a gap between the shoe and the piston. When the compressor is operated with a minimum discharge capacity, the compression reaction force and the suction force acting on the swash plate are minimized, and thus vibrations or noise may occur between the swash plate, the shoe and the piston. Such compressors mounted on vehicles may be offensive to the occupants.

The present invention is directed to a variable displacement swash plate type compressor which reduces the occurrence of vibration and noise in an operating state.

According to the present invention, a variable displacement swash plate compressor for compressing a refrigerant includes a housing, a drive shaft, a piston, a lug plate, a swash plate, a hinge mechanism, and a control mechanism. The housing forms a cylinder bore, a crank chamber, a suction chamber and a discharge chamber therein. The piston is reciprocally received in the cylinder bore to form a compression chamber in the cylinder bore. The drive shaft is driven by an external drive source and rotatably supported by the housing. The lug plate is supported by the drive shaft in the crank chamber to rotate with the drive shaft. The swash plate is supported by the drive shaft in the crank chamber. The hinge mechanism is provided between the lug plate and the swash plate. The swash plate can be inclined and rotated about the drive shaft through the lug plate and the hinge mechanism and reciprocates the piston through the shoe. The control mechanism controls the pressure in the crank chamber to change the discharge capacity of the refrigerant from the compression chamber to the discharge chamber by the reciprocating motion of the piston based on the inclination angle of the swash plate. The hinge mechanism is located on the suction side with respect to the first virtual plane including the top position of the swash plate corresponding to the top dead center position of the piston and the axis of the drive shaft, constrains the relative rotation of the lug plate and the swash plate, and at the same time the swash plate lugs And a restraining hinge that restrains movement in a direction away from the plate. The hinge mechanism further includes an unconstrained hinge that is located on the discharge side with respect to the first virtual plane and does not restrict the swash plate from moving in a direction away from the lug plate.

The novel features of the invention are set forth in the appended claims. The objects and advantages of the invention will be understood with reference to the following description of the preferred embodiments in conjunction with the accompanying drawings.

Best Mode for Carrying Out the Invention

 Hereinafter, exemplary embodiments of the present invention will be described with reference to FIGS. 1 to 7. Referring to FIG. 1, the variable displacement swash plate compressor 10 (hereinafter simply referred to as the “compressor”) of the preferred embodiment includes a housing 1, a single head piston 31, a drive shaft 16, a lug plate 24. And a swash plate 25 and a control mechanism 4. In FIG. 1, the left and right sides correspond to the front left and rear sides of the compressor 10, respectively.

The housing 1 is a cylinder block 11, a front housing 12 coupled to the front end of the cylinder block 11, a rear housing 13 coupled via a valve plate 14 to the rear end of the cylinder block 11. ) The front housing 12 and the rear housing 13 are fixed to the cylinder block 11 by bolts (not shown). The cylinder block 11 and the front housing 12 are combined to form a crank chamber 15 there.

The drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12. More specifically, the coil spring 17 and the thrust bearing 18 are arranged in the shaft hole 80 formed in the center of the cylinder block 11, and the rear end of the drive shaft 16 is connected to the coil spring 17. It is supported by the thrust bearing 18 urged forward. Further, the front end of the drive shaft 16 is supported by a radial bearing 19 disposed in the shaft hole 81 formed in the front housing 12. In addition, the sealing device 20 is formed in front of the radial bearing 19. Moreover, the pulley 21 provided through the bearing 90 is connected to the front end of the drive shaft 16 at the front end of the drive shaft 16. This pulley 21 is rotatable to the drive shaft 16. The pulley 21 is connected to the engine of the vehicle or the like as an external drive source via the belt 91. Thus, this compressor 10 is constantly driven by the engine during operation of the engine.

The lug plate 24 is press-fitted to the drive shaft 16 in the crank chamber 15. The thrust bearing 27 is formed between the lug plate 24 and the inner wall surface of the front housing 12. The swash plate 25 is attached to the drive shaft 16 and has a drawing hole 22 into which the drive shaft 16 is inserted. The drawing hole 22 is formed in the center of the swash plate 25, and has the parallel facing surface 23 which accommodates the outer peripheral surface of the drive shaft 16 as shown in FIG. 3 and FIG. The hinge mechanism 26 is formed between the lug plate 24 and the swash plate 25.

Referring to FIG. 1, a spring 28 is formed on the drive shaft 16 between the lug plate 24 and the swash plate 25. The spring 28 biases the swash plate 25 in the direction of approaching the cylinder block 11, that is, in a direction of decreasing the inclination angle of the swash plate 25. The circlip 29 is fixed on the drive shaft 16 behind the swash plate 25. A spring 30 is formed on the drive shaft 16 between the circlip 29 and the swash plate 25. When pressurized by the swash plate 25, the spring 30 urges the swash plate 25 away from the cylinder block 11, that is, in the direction of increasing the inclination angle of the swash plate 25.

In the cylinder block 11, the several cylinder bore 11a is formed so that the drive shaft 16 may be arrange | positioned at equal angle intervals. Only one cylinder bore 11a is shown. Each cylinder bore 11a extends in parallel to the drive shaft 16, and the piston 31 is disposed to reciprocate therein. The front end of each piston 31 is coupled to the outer periphery of the swash plate 25 via a pair of shoes 32. Each shoe 32 has a substantially hemispherical surface in contact with the piston 31, and has a flat surface in contact with the swash plate 25. A pair of shoes 32 are arranged on both sides of the swash plate 25 so that the shoes form a substantially spherical shape.

A compression chamber 33 is formed in each cylinder bore 11a between the piston head on the rear end side of the piston 31 and the valve plate 14. When the swash plate 25 is rotated by the drive shaft 16, the swash plate 25 is inclined with respect to the drive shaft 16, and the reciprocating motion of each piston 31 is carried out through a pair of shoes 32 to which the rocking motion of the swash plate 25 is related. Generate. Thus, the rotation of the drive shaft 16 is converted into the reciprocating motion of the piston 31 via the swash plate 25 and the shoe 32.

In the rear housing 13, the discharge chamber 34 and the annular suction chamber 35 surrounding the discharge chamber 34 are formed. The suction chamber 35 is connected to the downstream side of the refrigerating circuit 37 via the suction port 36 formed in the rear housing 13. The discharge chamber 34 is connected to the upstream side of the refrigerating circuit 37 formed in the rear housing 13 through the discharge port 38. The refrigeration circuit 37 includes a condenser 39, an expansion valve 40 and an evaporator 41.

The valve plate 14 has a suction port 42 and a discharge port 43 correspondingly arranged for each compression chamber 33. The valve plate 14 also has a suction valve 42a and a discharge valve 43a correspondingly disposed with respect to each suction port 42 and the discharge port 43. During the suction stroke of the piston 31, the refrigerant gas in the suction chamber 35 is sucked into the compression chamber 33 through the associated suction port 42 while pushing the suction valve 42a open. On the other hand, during the compression stroke of the piston 31, the refrigerant gas is compressed in the compression chamber, and then is discharged to the discharge chamber 34 through the associated discharge port 43 while pushing the discharge valve 43a open.

A supply passage 44 is formed to connect the crank chamber 15 and the discharge chamber 34 to the cylinder block 11, the valve plate 14 and the rear housing 13. A bleed passage 45 is formed to connect the crank chamber 15 and the suction chamber 35 to the cylinder block 11, the valve plate 14, and the rear housing 13. This bleed passage 45 has an orifice therein (not shown). As shown in FIG. 1, a displacement control valve 46 is disposed in the supply passage 44. For example, the displacement control valve 46 has a structure similar to the displacement control valve disclosed in Japanese Laid-Open Patent Publication No. 2003-239857. The supply passage 44, the bleed passage 45 and the displacement control valve 46 constitute a control mechanism 4 operable to control the pressure in the crank chamber 15.

The control mechanism 4 controls the opening and closing of the supply passage 44 by the capacity control valve 46 in accordance with the pressure change of the suction chamber 35, thereby increasing the pressure of the crank chamber 15 to thereby increase the compressor ( 10) Adjust the discharge capacity. When the cooling load is small and the pressure in the suction chamber 35 is low, the opening degree of the capacity control valve 46 is increased, whereby the pressure in the crank chamber 15 is increased, whereby the inclination angle of the swash plate 25 is audited. do. As a result, the stroke of each piston 31 is reduced, thereby reducing the discharge capacity of the compressor 10. On the other hand, when the cooling load is large and the pressure in the suction chamber 35 is high, the opening degree of the capacity control valve 46 is reduced, whereby the pressure in the crank chamber 15 is reduced, so that the swash plate 25 is The inclination angle is increased, the stroke of each piston 31 is increased, and the discharge capacity of the compressor 10 is increased. By the operating state such as acceleration of the vehicle, the opening degree of the capacity control valve 46 can be changed externally. The surface of the swash plate 25 facing toward the lug plate 24 provides a receiving surface 25a described later. The receiving surface 25a comes into contact with the lug plate 24, thereby adjusting the maximum inclination angle of the swash plate 25.

Next, the structure of the hinge mechanism 26 is demonstrated in detail. In the compressor 10 of the preferred embodiment, the drive shaft 16 is rotated in the direction indicated by the arrow Z in FIG. 1. Referring to FIG. 4, the CP represents a first virtual plane comprising the top position A of the swash plate 25 and the longitudinal axis O1 of the drive shaft 16. The uppermost position A of the swash plate 25 corresponds to the top dead center of the piston 31, and more particularly, arranges the piston 31 at the top dead center. The cross section taken along this first virtual plane CP substantially corresponds to the cross section of FIG. 1. SP in FIG. 4 represents a second imaginary plane extending perpendicular to the plane CP. This is because the swash plate 25 is inclined at the maximum inclination angle in Figs. Corresponds to the discharge side of the compressor. That is, in Fig. 1, the side and the back correspond to the discharge side and the suction side, respectively. In Fig. 2, the side and the back correspond to the suction side and the discharge side, respectively. That is, FIG. 1 is a sectional view of the compressor 10 showing the element located on the suction side with respect to the first virtual plane CP. 2 is an enlarged cross-sectional view of the compressor 10 showing the element located on the discharge side with respect to the first virtual plane CP.

As shown in FIG. 1, the hinge mechanism 26 is located on the suction side with respect to the first virtual plane CP and includes a support arm 61 and a guide pin 62 which act as a restraining hinge element 60. do. In addition, as shown in FIG. 2, the hinge mechanism 26 is located on the discharge side with respect to the first virtual plane CP, and serves as the first guide surface 71 and the second guide that act as non-binding hinges 70. Face 72. As shown in FIG. 3 and FIG. 4, the guide pin 62 and the second guide surface 72 are provided on the front surface of the swash plate 25. 1 and 2, the support arm 61 and the first guide surface 71 are provided on the rear side of the lug plate 24 facing toward the swash plate 25, and the guide pin 62 and It is arranged with respect to the second guide surface 72.

In the restraining hinge 60, the support arm 61 has a guide hole 61a having an inner circumferential surface, and the spherical portion 62a provided at the uppermost end of the guide pin 62 is slidable in the guide hole. Therefore, the support arm 61 and the guide pin 62 as the restraining hinge 60 restrain the relative rotation of the lug plate 24 and the swash plate 25, and the swash plate 25 is the lug plate 24. It acts to restrain movement in a direction away from it.

In the non-constrained hinge 70, the first guide surface 71 and the second guide surface 72 face each other and can also contact each other. The non-constrained hinge 70 does not include sidewalls for restraining relative rotation of the lug plate 24 and the swash plate 25, and restrains the swash plate 25 from moving in a direction away from the lug plate 24. It does not include a side wall. Accordingly, the first guide surface 71 and the second guide surface 72 as the non-constrained hinge 70 do not restrain the swash plate 25 from moving in the direction away from the lug plate 24, and thus the lug plate 24. ) And the relative rotation between the swash plate 25 are also not constrained.

According to the above configuration, when the non-constrained hinge element 70 is manufactured, the first guide surface 71 and the second guide surface for supporting the swash plate 25 to be inclined at a predetermined angle together with the restraining hinge 60. Only 72 may be formed with high precision. In addition, the positioning accuracy of the first guide surface 71 and the second guide surface 72 with respect to the restraining hinge element 60 may be lowered. Thus, unlike a pair of restraining hinges in the compressor disclosed in Japanese Patent Laid-Open No. 2917767, there is no need to enlarge the clearance between the support arm 61 and the guide pin 62 of the restraining hinge element 60. . Therefore, the clearance between these support arm 61 and the guide pin 62 can be manufactured small, and these support arm 61 and the guide pin 62 can be manufactured with the desired precision. More specifically, by securing the precision of the direction of the axis of the guide hole 61a and the guide pin 62, and the diameter of the guide hole 61a and the spherical part 62a, the guide hole 61a and the spherical part 62a are secured. Clearance can be made small easily. As a result, the swash plate 25 fits the restraining hinge 60 and the non-binding hinge 70 with a small clearance (or backlash).

Therefore, the restraining hinge 60 and the non-restraining hinge 70 of the hinge mechanism 26 are provided between the lug plate 24 and the swash plate 25 so that the swash plate 25 is at a predetermined inclination angle. For example, when the swash plate 25 is at the minimum inclination angle, as shown in FIGS. 5 and 6, the guide pin 62 of the restraining hinge 60 and the second guide surface of the non-restraining hinge 70 ( 72) The hinge mechanism 26 supports the swash plate 25 by slidingly positioned at a predetermined position.

Since the non-binding hinge 70 does not need a side wall for restraining the relative rotation between the lug plate 24 and the swash plate 25, the non-binding hinge 70 can be lightened.

Next, the receiving surface 25a of the swash plate 25 will be described in more detail. 1 to 4, the hinge mechanism 26 is located on the side of the uppermost position A with respect to the second virtual plane SP. On the swash plate 25 surface facing towards the lug plate 24, it is located on the suction side with respect to the first virtual plane CP, and the bottom position opposite to the top position A with respect to the second virtual plane SP. The receiving surface 25a located in (B) is formed. The bottom position B corresponds to the bottom dead center position of the piston 31. The receiving surface 25a is formed by machining the small area of the weight portion 25b of the swash plate 25 projecting from the swash plate 25 toward the lug plate 24 side smoothly. The receiving surface 25a is located within the range of the receiving surface 25a which can be in contact with the lug plate 24, and is located farthest from the axis O1 of the drive shaft 16, that is, as shown in FIG. 4. At the position furthest from the intersection between the center axis O2 passing through the axis of the hinge element 60 and the swash plate 25 and the axis O3 perpendicular to the axis O2 passing through the center of the receiving surface 25a Formed. In this way, as shown in FIG. 1, the receiving surface 25a is applied so that it may contact with the lug plate 24 and the swash plate 25 may not exceed a maximum inclination angle, as the swash plate 25 inclines at the largest inclination angle.

The compressor 10 of the above-described preferred embodiment constitutes a refrigeration circuit 37 of an automobile together with the condenser 39, the expansion valve 40, the evaporator 41, and the like. In the compressor 10, the drive shaft 16 is rotationally driven by an engine or the like as an external drive source, whereby through the restraining hinge 60 which restrains the relative rotation of the lug plate 24 and the swash plate 25, the swash plate ( 25) This rotates at a predetermined inclination angle. The rocking motion of the swash plate 25 is transmitted to the piston 31 via the shoe 32 so that the piston 31 is reciprocated in the associated cylinder bore 11a. Therefore, the refrigerant gas is sucked from the suction chamber 35 into the compression chamber 33 in the cylinder bore 11a, compressed, and discharged into the discharge chamber 34. The pressure in the crank chamber 15 is adjusted by the supply passage 44, the bleed passage 45, and the capacity control valve 46, and the inclination angle of the swash plate 25 is changed, whereby the pressure chamber 33 is released from the pressure chamber 33. The amount of refrigerant gas discharged to the discharge chamber 34 (or discharge capacity of the compressor 10) is controlled. Therefore, the cooling capacity according to the discharge capacity of the compressor 10 is realized by the refrigerating circuit 37.

During operation of the compressor 10, as shown in FIG. 7, the compression reaction force P1 and the suction force P2 of the refrigerant gas are applied to the swash plate 25 via the piston 31 and the shoe 32. The swash plate is urged so as to rotate around an intersection between the swash plate 25 and the first virtual plane CP to act as a moment M inclined with respect to the drive shaft 16. More specifically, this moment M is biased in the direction away from the lug plate 24 by the suction force P2 on the suction side of the first virtual plane CP, and the first virtual plane CP. ), The swash plate 25 is urged to press the lug plate 24 by the compression reaction force P1.

The support arm 61 and the guide pin 62 located on the suction side with respect to the first virtual plane CP restrain the swash plate 25 from moving in the direction away from the lug plate 24. Accordingly, the momentum M that biases the restraining hinge element 60 to move the swash plate 25 in a direction away from the lug plate 24 by the suction force P2 on the suction side with respect to the first virtual plane CP. Accept part of it.

The first guide surface 71 and the second guide surface 72 as the non-constrained hinge 70 pressurize the lug plate 24 by the compression reaction force P1 on the discharge side with respect to the first virtual plane CP. To receive a portion of the moment M to be obtained. Since a part of the moment M which biases the swash plate 25 to move away from the lug plate 24 by the suction force P2 is not applied to the non-constrained hinge element 70, the swash plate 25 is a lug plate. It is not necessary to restrain movement in the direction away from (24). The compressor 10 is operated at a high speed and a high capacity, for example, in a state in which refrigerant gas is insufficient in the refrigerating circuit 37, so that the inertia force of the piston 31 becomes excessively large, which further increases the inclination angle of the swash plate 25. When the moment M acts, the support arm 61 and the guide pin 62 as the restraining hinge 60 of the hinge mechanism 26 can receive the moment M. As shown in FIG. Therefore, this compressor 10 does not generate vibration and noise generated by the inclination angle of the swash plate 25 exceeding the maximum inclination angle. That is, the compressor 10 reduces the generation of vibration and noise during operation.

In the compressor 10 of the preferred embodiment, the restraining hinge 60 is formed in the lug plate 24, and is formed in the support arm 61 having the guide hole 61a having the inner circumferential surface, and in the swash plate 25. And a guide pin 62 having a spherical portion 62a capable of sliding in the hole 61a. When the guide pin 62 slides the guide hole 61a, the spherical portion 62a smoothly contacts the inner circumferential surface of the guide hole 61a to provide excellent durability to the hinge mechanism. Clearance between the guide hole 61a and the spherical portion 62a by ensuring the accuracy of the axis of the guide hole 61a and the direction of the axis of the guide pin 62 and the diameter of the guide hole 61a and the spherical portion 62a. Can be made small easily. As a result, the above-mentioned desirable effects of reducing the occurrence of noise and vibration can be more reliably obtained.

In the compressor 10 of the preferred embodiment, the non-constrained hinge element 70 does not restrain the relative rotation of the lug plate 24 and the swash plate 25, and is relative to the lug plate 24 and the swash plate 25. The part which restrains rotation becomes unnecessary. Therefore, in addition to the above-described effects, the weight is reduced, thereby improving the controllability of the compressor such as a response to the variation in the rotational speed of the drive shaft 16.

In the compressor 10 of the preferred embodiment, the non-constrained hinge 70 is formed on the lug plate 24, and is formed on the swash plate 25 and the first guide surface 71 facing toward the swash plate 25 side. And a second guide surface 72 facing toward the first guide surface 71. When the non-constrained hinge element 70 is manufactured, only the first guide face 71 and the second guide face 72 need to be manufactured with high precision, so that the manufacture of the non-constrained hinge element 70 becomes easy, and the compressor ( The manufacturing cost of 10 can be further reduced.

In the compressor 10 of the preferred embodiment, the hinge mechanism 26 is located on the top position A side with respect to the second virtual plane SP. This stabilizes the top dead center position of the piston 31 regardless of the inclination angle. Therefore, the capacity (or top clearance) of the compression chamber 33 formed by the head of the piston 31 located at the top dead center becomes small, whereby the re-expansion of the refrigerant gas in the compression chamber 33 can be suppressed. have.

Further, in a preferred embodiment, the swash plate 25 is moved by the restraining hinge element 60 which is on the top position A side with respect to the second virtual plane SP and on the suction side with respect to the first virtual plane CP. To redeem. The center swash plate 25 constrains the movement by the parallelly facing surfaces 23 of the stretching holes 22. However, the swash plate 25 does not restrain the rotation about the axis O2. When the compressor 10 is operated at a low speed, the combined force of the compression reaction force and the inertia force of the piston 31 is the discharge side with respect to the first virtual plane CP and the top position A with respect to the second virtual plane SP. It is applied to the swash plate 25. That is, the force presses a part of the swash plate 25 adjacent to the non-constrained hinge element 70 and presses against the lug plate 24, ie, the second guide surface 72 is away from the first guide surface 71. The swash plate 25 is stably supported by being urged to move.

When the compressor 10 operates at high speed, for example, when the rotational speed of the drive shaft 16 is increased (eg, 4000 to 5000 rpm or more), the force is the highest position A with respect to the second virtual plane SP. It is applied to the swash plate 25 at the bottom position B side opposite to. That is, the force forces a part of the swash plate 25 adjacent to the non-constrained hinge element 70 in a direction away from the lug plate 24, that is, the second guide surface 72 is separated from the first guide surface 71. To the direction. However, the surface of the swash plate 25 facing the lug plate 24 is the receiving surface positioned on the suction side with respect to the first virtual plane CP and on the bottom position B side with respect to the second virtual plane SP. Provide 25a. When the rotational speed of the drive shaft 16 is increased (for example, 4000 to 5000 rpm or more), and the swash plate 25 is inclined at the maximum inclination angle, the receiving surface 25a is pressed against the lug plate 24. Thus, the right upper part of the swash plate 25 is constrained away from the lug plate 24 with respect to a portion of the swash plate 25 adjacent to the non-constrained hinge element 70, that is, the axis O 2 shown in FIG. 4.

It is preferable that the receiving surface 25a be made smaller as long as it is a length located within the above-mentioned contactable range. If the receiving surface 25a is formed in a large area, the small area of the receiving surface 25a can actually contact the lug plate 24 due to the tolerance at the time of assembly. In addition, the large area of the receiving surface 25a increases the manufacturing cost due to high accuracy machining.

In the compressor 10 of the preferred embodiment, the receiving surface 25a is easily formed in the weight portion 25b of the swash plate 25. This contributes to the reduction of the manufacturing cost.

Since the receiving surface 25a is formed at the position farthest from the axis O1 of the drive shaft 16 in the range that can be in contact with the lug plate 24, the first guide surface 71 and the second guide surface Appropriately receives the force which moves the swash plate 25 in the direction which 72 moves away from each other.

The compressor 10 of the preferred embodiment is mounted in a vehicle so that the drive shaft 16 is constantly driven when the engine of the vehicle is being driven. Thus, compressor 10 often operates with a minimum discharge capacity. Thus, the compressor 10 improves the reduction of vibration and noise, which is one of the desirable effects of the present invention.

In the compressor 10 of the preferred embodiment, the swash plate 25 includes a drawing hole 22 which is received by a surface 23 facing the outer circumferential surface of the drive shaft 16 in parallel. This reduces the manufacturing cost compared to the case of forming a sleeve between the drive shaft 16 and the swash plate 25. The parallelly facing surfaces 23 of the stretching holes 22 rotate about the intersection of the swash plate 25 and the first virtual plane CP by the compression reaction force P1 and the suction force P1, and thus the swash plate 25. ) Receives a portion of the moment M, which biases to tilt the drive shaft 16. However, as described above, most of the moment M is received by the restraining hinge element 60 and the non-constrained hinge element 70. Therefore, the parallel opposing surfaces 23 of the drawing holes 22 smoothly contact the drive shaft 16, whereby wear between them is suppressed.

Alternatively, a sleeve may be provided between the swash plate 25 and the drive shaft 16. Like the hinge mechanism 26, the sleeve may support the swash plate 25, and may be inclined with respect to the drive shaft 16 disclosed in Japanese Patent Laid-Open No. 6-123281. Moreover, this sleeve is slidable in the axial direction of the drive shaft 16 with respect to the outer circumference of the coaxial shaft 16. This sleeve receives a portion of the moment M that biases the swash plate 25 so as to rotate around the intersection between the swash plate 25 and the first virtual plane CP.

Optionally, the support arm 61 is provided on the swash plate 25, and the guide pin 62 may be provided on the lug plate 24. The first guide surface 71 may be provided on the swash plate 25, and the second guide surface 72 may be provided on the lug plate 24.

The examples and embodiments of the invention are intended to be illustrative and not restrictive, and the invention is not to be limited to the foregoing detailed description, but may be modified within the scope of the appended claims.

As described above, according to the present invention, there is provided a variable displacement swash plate compressor for reducing the occurrence of vibration and noise in the operating state.

Claims (10)

A housing which forms a cylinder bore, a crank chamber, a suction chamber and a discharge chamber therein, A piston reciprocally received in the cylinder bore to form a compression chamber in the cylinder bore, A drive shaft driven by an external drive source and rotatably supported by the housing; A lug plate supported by the drive shaft in the crank chamber to rotate with the drive shaft, A swash plate supported by the drive shaft in the crank chamber, A hinge mechanism provided between the lug plate and the swash plate, The swash plate can be tilted and rotated relative to the drive shaft via the lug plate and the hinge mechanism and reciprocates the piston through the shoe, A variable capacity type for compressing a refrigerant having a control mechanism for controlling the pressure in the crank chamber to change the discharge capacity of the refrigerant from the compression chamber to the discharge chamber by the reciprocating motion of the piston based on the inclination angle of the swash plate. In the swash plate type compressor, The hinge mechanism is located on the suction side with respect to a first virtual plane including a top position of the swash plate corresponding to a top dead center position of the piston and an axis of the drive shaft, to restrain relative rotation of the lug plate and the swash plate. And a constraining hinge that restrains the swash plate from moving in a direction away from the lug plate, wherein the hinge mechanism is located on the discharge side with respect to the first virtual plane so that the swash plate is away from the lug plate. A variable displacement swash plate compressor further comprising a non-restraining hinge that does not restrain movement in the direction. The guide hinge of claim 1, wherein the restraining hinge is formed in one of the lug plate and the swash plate, and is formed in a guide hole having an inner circumferential surface, and the other of the lug plate and the swash plate, and sliding in the guide hole. A variable displacement swash plate type compressor comprising a guide pin having a spherical shape. The variable displacement swash plate compressor of claim 1, wherein the non-constrained hinge is provided so as not to restrain relative rotation between the lug plate and the swash plate. The said non-constrained hinge is a said 1st guide surface formed in one side of the said lug plate and the said swash plate, and the said lug which faces toward the said 1st guide surface, And a second guide surface formed on the other side of the plate and the swash plate and in contact with the first guide surface. 2. The hinge mechanism of claim 1, wherein the hinge mechanism is positioned at an uppermost position side of the swash plate with respect to a second virtual plane that includes an axis of the drive shaft and is orthogonal to the first virtual plane, and faces toward the lug plate of the swash plate. On the face of the swash plate, the suction side with respect to the first virtual plane and on the side opposite to the top position with respect to the second virtual plane, in contact with the lug plate and thereby thereby A variable displacement swash plate type compressor comprising a receiving surface for regulating the maximum inclination angle of the swash plate to the maximum inclination angle. 6. The variable displacement swash plate compressor of claim 5, wherein the receiving surface is formed in a weight portion provided on the swash plate. 6. The variable displacement swash plate compressor of claim 5, wherein the receiving surface is in a range in contact with the lug plate, and is formed at a position farthest from an axis of the drive shaft. The variable displacement swash-plate compressor according to claim 1, wherein the drive shaft is constantly driven while the external drive source is being driven. The variable displacement swash plate type compressor according to claim 1, wherein the swash plate has a drawing hole accommodated by a surface facing the outer circumferential surface of the drive shaft in parallel. The capacity of claim 1, wherein the control mechanism includes a supply passage connecting the discharge chamber to the crank chamber, a bleed passage connecting the crank chamber to the suction chamber, and a capacity control valve disposed in the supply passage. Variable swash plate compressor.

Images