JP2005090365A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To smoothly and relatively move a rotor side hinge part and a cam plate side hinge part when changing discharge capacity even if a cam plate is inclined in the direction different from the direction for changing discharge capacity. <P>SOLUTION: Side faces 42a, 43a of a first rotor side projection 42 and a second rotor side projection 43 and a cam face 47a of a cam part 47 guide relative moving of a projecting part 44. A first holding spherical face 51a is formed by opposing to the cam face 47a in the projecting part 44, and a second holding spherical face 52a and a third holding spherical face 53a are formed by opposing to side faces 45a, 46a. A first shoe 61 has a slide-contact plane 61b brought into contact with the cam face 47a in a plane and a slide-contact spherical face 61a received by the first holding spherical face 51a on a spherical face. A second shoe 62 and a third shoe 63 have slide-contact planes 62b, 63b brought into contact with the side faces 42a, 43a in planes and slide-contact spherical faces 62a, 63a received by the second and third holding spherical faces 52a, 53a on spherical faces. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a variable capacity compressor constituting a refrigeration circuit of a vehicle air conditioner, for example.

  As this type of variable capacity compressor, there is one as shown in FIG. 6 (see, for example, Patent Document 1). In the variable displacement compressor, the rotational movement of the drive shaft 82 is converted into the reciprocating movement of the piston 86 via the rotor 83, the hinge mechanism 85, and the cam plate (swash plate) 84, and the refrigerant gas is compressed. . Further, the cam plate 84 is slid and moved on the drive shaft 82 by the guidance of the hinge mechanism 85, so that the tilt angle can be changed. In accordance with the change in the inclination angle of the cam plate 84, the stroke of the piston 86, that is, the discharge capacity of the variable displacement compressor is changed.

  As shown in FIG. 7, the hinge mechanism 85 includes two arms 87 and 88 extending from the cam plate 84 toward the rotor 83, and extending from the rotor 83 toward the cam plate 84 and between the two arms 87 and 88. And a protrusion 89 inserted into the. When the rotor 83 rotates in the direction of the arrow R, the rotational force T from the rotor 83 to the cam plate 84 between the side surface 88a of one arm 88 and the side surface 89a facing the side surface 88a of the arm 88 at the protrusion 89. Transmission takes place. In this state, there is a slight gap between the side surface 87a of the other arm 87 that does not bear power transmission and the side surface 89b of the protrusion 89 facing the side surface 87a of the arm 87 due to dimensional tolerances or the like. Will be formed. The gap is exaggerated in the drawing.

  As shown in FIGS. 6 and 7, columnar surfaces 87b and 88b are formed at the tips of the arms 87 and 88 perpendicular to the side surfaces 87a and 88a. In the rotor 83, a cam portion 90 having a cam surface 90 a with which the column surfaces 87 b and 88 b of the arms 87 and 88 come into contact is formed at the base of the protrusion 89. The axial load caused by the compression reaction force F acting on the cam plate 84 along the axis L of the drive shaft 82 is caused by the column surfaces 87b and 88b of the arms 87 and 88 and the cam surface 90a of the cam portion 90. It is received by the rotor 83.

  When the variable displacement compressor increases the discharge capacity, the cam plate 84 is rotated in the clockwise direction in FIG. 6 with the cylindrical center S of the column surfaces 87b and 88b of the arms 87 and 88 as axes. . At the same time, the tips of the arms 87 and 88 are moved in a direction away from the drive shaft 82 on the cam surface 90 a of the cam portion 90, so that the hinge mechanism 85 guides the increase in the inclination angle of the cam plate 84. Conversely, when the variable displacement compressor reduces the discharge capacity, the cam plate 84 is rotated in the counterclockwise direction of FIG. 6 with the cylinder center S of the column surfaces 87b and 88b as the axis. At the same time, the tips of the arms 87 and 88 are moved on the cam surface 90 a of the cam portion 90 in the direction approaching the drive shaft 82, so that the hinge mechanism 85 guides the decrease in the inclination angle of the cam plate 84.

  However, in the embodiment shown in FIGS. 6 and 7, the arms 87 and 88 on the cam plate 84 side, the protrusion 89 and the cam portion 90 on the rotor 83 side are in direct contact with each other. Accordingly, the column surfaces 87b and 88b of the arms 87 and 88, which are axial load transmission portions, and the cam surface 90a of the cam portion 90 are in line contact with each other. There is a problem that the contact slidability between the surface 90a and the column surfaces 87b and 88b is lowered, and the tilting of the cam plate 84 is not smooth, and the capacity controllability of the variable capacity compressor is deteriorated.

In order to solve such a problem, for example, as shown by a two-dot chain line in the enlarged circle of FIG. 6, a shoe is interposed between the cam surface 90a of the cam portion 90 and the column surfaces 87b and 88b of the arms 87 and 88. 95 may be interposed (see, for example, Patent Document 2). The shoe 95 has a sliding contact surface 95a that contacts the cam surface 90a, and a sliding contact concave surface 95b that contacts the column surfaces 87b and 88b of the arms 87 and 88 along the column surfaces 87b and 88b. . Therefore, the contact between the cam surface 90a and the shoe 95 (sliding contact flat surface 95a) and the contact between the shoe 95 (sliding contact concave surface 95b) and the column surfaces 87b and 88b are surface contacts. Therefore, load resistance between the column surfaces 87b, 88b of the arms 87, 88 and the cam surface 90a of the cam portion 90 can be improved, and the movement of the column surfaces 87b, 88b relative to the cam surface 90a, that is, the cam plate. 84 can be smoothly tilted, and the capacity controllability of the variable capacity compressor can be improved.
JP 2001-304102 A (3rd and 4th pages, FIGS. 1 to 3) JP-A-9-203377 (5th page, FIG. 1)

  Here, as shown in FIG. 7, the cam plate 84 has a half-circumference portion on the compression stroke side, that is, a top dead center corresponding portion TDC and a virtual plane H including the axis L of the drive shaft 82 as a boundary. Due to the compression reaction force F, the left-side half-circular portion receives a reaction force so as to be pushed from the piston 86 to the rotor 83 side. Further, the cam plate 84 has a half-circumference portion on the suction stroke side, that is, a half-circumference portion on the right side in FIG. 7 bordering on the plane H, pulled to the opposite side of the rotor 83 due to the suction of the refrigerant gas. The piston 86 receives a force. Therefore, as shown by a two-dot chain line in FIG. 7, the cam plate 84 may be inclined in a direction different from the direction in which the discharge capacity is changed.

  Therefore, in the hinge mechanism 85 of Patent Document 1, one arm 88 hits the cam surface 90a of the cam portion 90 and the side surface 89a of the projection 89, or the projection 89 corners the side surface 87a of the other arm 87. There is a problem to hit. Therefore, the contact sliding property between the arms 87 and 88 and the projection 89 and the cam portion 90 at the time of changing the discharge capacity is deteriorated, the durability of the hinge mechanism 85 is lowered, or the arms 87 and 88 and the projection 89 and There has been a problem that the relative movement with the cam portion 90 is not smooth, that is, the capacity controllability of the variable capacity compressor is deteriorated.

  This problem cannot be solved when the technique of Patent Document 2 is adopted. In other words, the sliding contact concave surface 95b of the shoe 95 and the column surfaces 87b and 88b of the arms 87 and 88 are in contact with a cylindrical surface. Accordingly, the surface contact between the cam surface 90a of the cam portion 90 and the sliding contact plane 95a of the shoe 95 and the surface contact between the sliding contact concave surface 95b of the shoe 95 and the column surfaces 87b and 88b of the arms 87 and 88 are maintained by the cam. This can be realized only when the plate 84 rotates about the columnar center S of the column surfaces 87b and 88b. Therefore, when the cam plate 84 is inclined in a direction different from the direction in which the discharge capacity is changed, the surface contact between the column surfaces 87b and 88b of the arms 87 and 88 and the sliding contact concave surface 95b of the shoe 95 and the sliding contact plane of the shoe 95 are achieved. As a result, at least one of the surface contact between 95a and the cam surface 90a of the cam portion 90 is not maintained, and the corner contact problem substantially similar to the hinge mechanism 85 of Patent Document 1 occurs.

  That is, in the related art, a shoe 95 is interposed between the cam surface 90a of the cam portion 90 and the column surfaces 87b and 88b of the arms 87 and 88, so that the durability of the hinge mechanism 85 and the capacity of the variable displacement compressor are achieved. The idea of improving controllability has been disclosed. However, it has not been taken into consideration even when the cam plate 84 is inclined in a direction different from the direction in which the discharge capacity is changed.

  An object of the present invention is to make the relative movement between the rotor side hinge part and the cam plate side hinge part smooth when changing the discharge capacity even when the cam plate is inclined in a direction different from the direction in which the discharge capacity is changed. It is an object of the present invention to provide a variable capacity compressor capable of achieving the above.

  In order to achieve the above object, the capacity variable compressor according to claim 1 is configured such that the first hinge portion, which is one of the rotor side hinge portion and the cam plate side hinge portion, constituting the hinge mechanism has a second one which is the other. A guide plane for guiding the relative movement of the hinge portion is formed. A holding spherical surface is formed on the second hinge portion so as to face the guide plane. The shoe has a sliding contact plane that is in plane contact with the guide plane of the first hinge portion, and a sliding contact spherical surface that is spherically received by the holding spherical surface of the second hinge portion.

  The spherical receiving structure of the holding spherical surface of the second hinge part and the sliding contact spherical surface of the shoe has a discharge capacity in addition to the relative rotation of the second hinge part and the shoe with the tilt of the cam plate when the discharge capacity is changed. Relative rotation of the second hinge portion and the shoe is allowed with the tilting of the cam plate in a direction different from the changing direction. Therefore, even when the cam plate is inclined in a direction different from the direction in which the discharge capacity is changed, the surface contact between the guide plane of the first hinge part and the sliding contact plane of the shoe, and the sliding contact spherical surface of the shoe and the second hinge part Surface contact with the holding spherical surface can be maintained. Therefore, even when the cam plate is inclined in a direction different from the direction in which the discharge capacity is changed, the relative movement between the rotor side hinge part and the cam plate side hinge part when the discharge capacity is changed can be made smooth.

  According to a second aspect of the present invention, in the first aspect, the second hinge part has a protruding shape, and the first hinge part has a tip of the second hinge part accompanying the tilting of the cam plate when the discharge capacity is changed. A cam surface for guiding the relative movement of the cam is formed. The cam surface forms a guide plane. The holding spherical surface is formed at the tip of the second hinge portion, and the axial load acting on the cam plate along the axis of the drive shaft is received by the rotor via the guide plane, the shoe and the holding spherical surface.

  For example, in the hinge mechanism of Patent Document 1, the portion transmitting the axial load is determined based on the magnitude of the load from the rotor side hinge (cam portion 90 (see FIG. 7)) and the cam plate side hinge (arm 88 (see FIG. 7). 7))), the smooth relative movement between the rotor-side hinge portion and the cam plate-side hinge portion is greatly hindered. Therefore, the shoe is interposed in the portion, and the surface contact between the shoe and the first hinge portion and between the shoe and the second hinge portion is different from the direction in which the cam plate changes the discharge capacity. The fact that it can be maintained even in a tilted state is particularly effective in smoothing the relative movement between the rotor-side hinge portion and the cam plate-side hinge portion.

  According to a third aspect of the present invention, in the first aspect, the first hinge part is formed with a power transmission surface that transmits power to and from the second hinge part. The power transmission surface forms a guide plane. The holding spherical surface is formed on the power transmission surface on the second hinge portion side facing the guide plane. The rotational force of the rotor is transmitted to the cam plate through the guide plane, the shoe and the holding spherical surface.

  For example, in the hinge mechanism of Patent Document 1, a portion that transmits power is divided into a rotor-side hinge portion (projection 89 (see FIG. 7)) and a cam plate-side hinge portion (arm 88 (see FIG. 7) due to the magnitude of the transmitted power. )), The smooth relative movement between the rotor-side hinge portion and the cam plate-side hinge portion is greatly hindered. Therefore, the shoe is interposed in the portion, and the surface contact between the shoe and the first hinge portion and between the shoe and the second hinge portion is different from the direction in which the cam plate changes the discharge capacity. The fact that it can be maintained even in a tilted state is particularly effective in smoothing the relative movement between the rotor-side hinge portion and the cam plate-side hinge portion.

  The invention of claim 4 refers to an example of the interposition position of the shoe in claim 1. One of the rotor side hinge portion and the cam plate side hinge portion includes two wall portions. The other of the rotor side hinge part and the cam plate side hinge part has a protrusion inserted between the two wall parts. Of the side surfaces of the first hinge portion that face the side surfaces of the second hinge portion, the side surface that is not on the power transmission side forms a guide plane. The holding spherical surface is formed on a side surface that is opposed to the guide plane in the second hinge portion and is not on the power transmission side.

  According to a fifth aspect of the present invention, in the first aspect, the second hinge portion has a projecting shape, and the first hinge portion has a second hinge portion that accompanies tilting of the cam plate corresponding to a change in discharge capacity. A cam surface for guiding the relative movement of the tip is formed. The cam surface forms a first guide plane. The first holding spherical surface is formed at the tip of the second hinge portion. An axial load acting on the cam plate along the axis of the drive shaft is received by the rotor via the first guide plane, the first shoe and the first holding spherical surface.

  The first hinge portion is formed with a power transmission surface that transmits power to and from the second hinge portion. The power transmission surface forms a second guide plane. The second holding spherical surface is formed on the power transmission surface on the second hinge portion side facing the second guide plane. The rotational force of the rotor is transmitted to the cam plate through the second guide plane, the second shoe, and the second holding spherical surface.

  As described above, in the hinge mechanism, the shoe is interposed in each of the portion transmitting the axial load and the portion transmitting the power, and further, between each shoe and the first hinge portion and between each shoe and the second hinge portion. Can be maintained even when the cam plate is inclined in a direction different from the direction in which the discharge capacity is changed, in order to make the relative movement between the rotor side hinge and the cam plate side hinge smooth. Especially effective.

  A sixth aspect of the present invention is that in the fifth aspect, one of the rotor side hinge portion and the cam plate side hinge portion includes two wall portions. The other of the rotor side hinge part and the cam plate side hinge part has a protrusion inserted between the two wall parts. Of the side surfaces of the first hinge portion that face the side surfaces of the second hinge portion, the side surface that is not on the power transmission side forms a third guide plane. The third holding spherical surface is formed on a side surface that is opposed to the third guide plane in the second hinge portion and is not on the power transmission side. A third shoe is interposed between the third guide plane and the third holding spherical surface.

  In this way, the third shoe is also interposed between the side surfaces that are not on the power transmission side, and further, the surface between the third shoe and the first hinge portion and between the third shoe and the second hinge portion. The fact that the contact can be maintained even when the cam plate is tilted in a direction different from the direction in which the discharge capacity is changed is particularly effective in smoothing the relative movement between the rotor side hinge portion and the cam plate side hinge portion.

  According to the present invention, even when the cam plate is inclined in a direction different from the direction in which the discharge capacity is changed, the relative movement between the rotor side hinge part and the cam plate side hinge part when the discharge capacity is changed is made smooth. Is possible. Therefore, the variable capacity compressor can improve the durability of the hinge mechanism and also improve the capacity controllability.

Hereinafter, an embodiment in which the present invention is embodied in a variable capacity compressor constituting a refrigeration circuit of a vehicle air conditioner will be described.
(Basic configuration of variable capacity compressor)
FIG. 1 shows a longitudinal section of a variable capacity compressor (hereinafter simply referred to as a compressor). In FIG. 1, the left side is the front of the compressor and the right side is the rear of the compressor.

  As shown in FIG. 1, a compressor housing (compressor housing) includes a cylinder block 11, a front housing 12 joined and fixed to the front end of the cylinder block 11, and a valve / port formed at the rear end of the cylinder block 11. And a rear housing 14 joined and fixed through a body (valve assembly) 13.

  A crank chamber 15 is defined between the cylinder block 11 and the front housing 12. A drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15.

  The drive shaft 16 is operatively connected to an engine E, which is a vehicle drive source, via a power transmission mechanism PT. The power transmission mechanism PT may be a clutch mechanism (for example, an electromagnetic clutch) capable of selecting transmission / cutoff of power by electric control from the outside, or a constant power transmission clutch that does not have such a clutch mechanism. A less mechanism (for example, a belt / pulley combination) may be used. In the present embodiment, a clutchless type power transmission mechanism PT is employed. Accordingly, when the engine E is in operation, the drive shaft 16 is always rotated by receiving power from the engine E.

  In the crank chamber 15, a substantially disc-shaped rotor 17 is fixed to the drive shaft 16 so as to be integrally rotatable. In the crank chamber 15, a swash plate 18 as a cam plate, which is substantially disk-shaped, is accommodated. The swash plate 18 is supported by the drive shaft 16 so as to be slidable and tiltable by inserting the drive shaft 16 through an insertion hole (not shown) formed through the central portion.

  A hinge mechanism 19 is provided between the rotor 17 and the swash plate 18. The hinge mechanism 19 rotates the swash plate 18 synchronously with the rotor 17 and the drive shaft 16 and allows the swash plate 18 to slide on the drive shaft 16 along the axis L of the drive shaft 16.

  In the cylinder block 11, a plurality of cylinder bores 22 are formed at equal angular intervals around the axis L of the drive shaft 16. The cylinder bore 22 extends along the axis L of the drive shaft 16. Each cylinder bore 22 accommodates a single-headed piston 23 so as to be able to reciprocate. The front and rear openings of the cylinder bore 22 are respectively closed by the front end surface 13a of the valve / port forming body 13 and the corresponding piston 23, and a compression chamber 24 whose volume changes in accordance with the reciprocating motion of the piston 23 is defined in the cylinder bore 22. Has been. Each piston 23 is anchored to the outer peripheral portion of the swash plate 18 via a pair of hemispherical shoes 25. Therefore, the rotational motion of the swash plate 18 accompanying the rotation of the drive shaft 16 is converted into the reciprocating linear motion of each piston 23 via both shoes 25.

  A suction chamber 26 and a discharge chamber 27 are defined between the valve / port forming body 13 and the rear housing 14, respectively. The valve / port forming body 13 has a suction port 28, a suction valve 29, a discharge port 30, and a discharge valve 31 corresponding to the cylinder bores 22. The refrigerant gas in the suction chamber 26 is sucked into the compression chamber 24 through the suction port 28 and the suction valve 29 as each piston 23 moves from the top dead center position toward the bottom dead center position. The refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure as the piston 23 moves from the bottom dead center position to the top dead center position, and the discharge port 30 and the discharge valve 31 are made to flow. Through the discharge chamber 27.

(Compressor capacity control structure)
As shown in FIG. 1, an extraction passage 32, an air supply passage 33, and a control valve 34 are provided in the compressor housing. The extraction passage 32 connects the crank chamber 15 and the suction chamber 26. The air supply passage 33 connects the discharge chamber 27 and the crank chamber 15. The control valve 34 made of an electromagnetic valve is disposed in the middle of the air supply passage 33.

  The amount of high-pressure refrigerant gas introduced from the discharge chamber 27 into the crank chamber 15 through the air supply passage 33 and the crank are adjusted by adjusting the opening degree of the control valve 34 by power supply control to the control valve 34 from the outside. The balance with the amount of gas derived from the chamber 15 to the suction chamber 26 via the extraction passage 32 is controlled, and the internal pressure of the crank chamber 15 is determined. As the internal pressure of the crank chamber 15 is changed, the difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 24 is changed, and the inclination angle of the swash plate 18 is changed accordingly. The discharge capacity of the machine is adjusted. The inclination angle of the swash plate 18 is an angle formed between a plane orthogonal to the axis L of the drive shaft 16.

  For example, when the opening degree of the control valve 34 decreases, the internal pressure of the crank chamber 15 decreases. Then, the inclination angle of the swash plate 18 increases, the stroke of the piston 23 increases, and the discharge capacity of the compressor increases. The maximum inclination angle of the swash plate 18 is defined by the protrusion 18 a protruding from the front surface of the swash plate 18 contacting the rear surface of the rotor 17.

  Conversely, as the valve opening of the control valve 34 increases, the internal pressure of the crank chamber 15 increases. Then, the inclination angle of the swash plate 18 decreases, the stroke of the piston 23 decreases, and the discharge capacity of the compressor decreases.

(Hinge mechanism)
As shown in FIG. 1, the swash plate 18 has a top dead center corresponding portion TDC on the same side as the hinge mechanism 19 with respect to the drive shaft 16. Each piston 23 is disposed at the top dead center position when facing the top dead center corresponding site TDC of the swash plate 18. The top dead center corresponding portion TDC includes the center points of the spherical surfaces of the shoes 25 corresponding to the piston 23 at the top dead center position. As shown in FIGS. 1 and 2, an engagement groove 41 is formed on the rear surface of the rotor 17 at a position facing the top dead center corresponding portion TDC of the swash plate 18.

  The engagement groove 41 is formed by first and second rotor side protrusions 42 and 43 as wall portions extending from the rear surface of the rotor 17 toward the swash plate 18. The first rotor-side protrusion 42 is disposed on the subsequent side in the rotation direction of the rotor 17 (the direction indicated by the arrow R in FIG. 2 in this embodiment) with respect to the engagement groove 41. The second rotor-side protrusion 43 is disposed on the leading side in the rotation direction of the rotor 17 with respect to the engagement groove 41. The first and second rotor-side protrusions 42 and 43 have side surfaces 42 a and 43 a that face each other in the engagement groove 41.

  A protrusion 44 as a cam plate side hinge portion extending toward the rotor 17 is provided at a portion of the front surface of the swash plate 18 facing the engagement groove 41. The protrusion 44 is constituted by first and second swash plate side protrusions 45 and 46. The first swash plate side protrusion 45 is disposed on the subsequent side with respect to the top dead center corresponding portion TDC in the rotation direction of the drive shaft 16. The second swash plate side protrusion 46 is disposed on the leading side with respect to the top dead center corresponding part TDC in the rotation direction of the drive shaft 16. That is, the protrusion 44 has a hollow structure in which the two swash plate side protrusions 45 and 46 are left on both sides in order to reduce the weight of the swash plate 18. In FIG. 2, the clearance between the first and second rotor side protrusions 42 and 43 and the protrusion 44 is exaggerated.

  The first and second swash plate side protrusions 45 and 46 are inserted into the engagement groove 41. The first and second swash plate side protrusions 45 and 46 have side surfaces 45a and 46a facing opposite sides. In other words, the side surface 45 a of the first swash plate side protrusion 45 is opposed to the side surface 42 a of the first rotor side protrusion 42. The side surface 46 a of the second swash plate side protrusion 46 is opposed to the side surface 43 a of the second rotor side protrusion 43.

  A cam portion 47 bulges out at the base portion of the second rotor-side protrusion 43 in the engagement groove 41. A cam surface 47 a is formed on the rear end surface facing the swash plate 18 in the cam portion 47 so as to incline toward the rear side as it approaches the axis L of the drive shaft 16.

  The first and second rotor-side protrusions 42 and 43 and the cam portion 47 constitute a rotor-side hinge portion. One of the rotor side hinge part and the cam plate side hinge part (projecting part 44) constitutes a first hinge part, and the other constitutes a second hinge part. In the present embodiment, the rotor-side hinge portion (the first and second rotor-side protrusions 42 and 43 and the cam portion 47) constitutes the first hinge portion, and the protrusion 44 constitutes the second hinge portion.

(Shoe in hinge mechanism)
A first shoe seat 51 is recessed at a portion of the tip of the second swash plate side protrusion 46 that is close to the side surface 46a. The first shoe seat 51 is formed with a first holding spherical surface 51 a as a first holding spherical surface that is a concave surface facing the cam surface 47 a of the cam portion 47. Between the first holding spherical surface 51a and the cam surface 47a, a first shoe 61 is disposed as a first hemispherical shoe. The first shoe 61 has a slidable contact surface 61b that is in plane contact with the cam surface 47a, and a slidable contact spherical surface 61a that is spherically received by the first holding spherical surface 51a. Therefore, the tip of the second swash plate side protrusion 46 and the cam portion 47 are slidably contacted and engaged via the first shoe 61.

  The cam surface 47 a of the cam portion 47 receives the axial load acting on the swash plate 18 due to the compression reaction force F caused by the piston 23 compressing the refrigerant gas in the compression chamber 24. From the first shoe 61.

  On the side surface 45a of the first swash plate side projection 45, a second shoe seat 52 is recessed on the tip side of the first swash plate side projection 45. The second shoe seat 52 is formed with a second holding spherical surface 52a as a second holding spherical surface that is a concave surface facing the side surface 42a of the first rotor-side protrusion 42. Between the second holding spherical surface 52a and the side surface 42a of the first rotor side protrusion 42, a second shoe 62 as a second shoe having a hemispherical shape is disposed. The second shoe 62 has a slidable contact surface 62b that is in plane contact with the side surface 42a of the first rotor side protrusion 42, and a slidable contact spherical surface 62a that is spherically received by the second holding spherical surface 52a. Therefore, the first rotor side protrusion 42 and the first swash plate side protrusion 45 are slidably contacted and engaged via the second shoe 62.

  Note that the second shoe seat 52 and the second shoe 62 in FIG. 1 are easier to see by not overlapping the first shoe seat 51 and the first shoe 61. The side projection 45 is shown shifted to the base side.

  As the drive shaft 16 rotates in the direction of arrow R, the rotational force T of the rotor 17 is driven from the side surface 42a of the first rotor side protrusion 42 through the second shoe 62 to the power of the first swash plate side protrusion 45. It is transmitted to the side surface 45a which is a transmission surface. That is, the side surface 42 a of the first rotor side protrusion 42 forms a power transmission surface that transmits power to the first swash plate side protrusion 45, and the side surface 45 a transmits power to the first swash plate side protrusion 45. It has a surface.

  A third shoe seat 53 is recessed on the base side of the second swash plate side projection 46 on the side surface 46a of the second swash plate side projection 46, which is the side surface of the side surfaces 45a and 46a that is not the power transmission side. . The third shoe seat 53 is formed with a third holding spherical surface 53a as a third holding spherical surface that is a concave surface facing the side surface 43a of the second rotor side protrusion 43 that is not on the power transmission side. Between the third holding spherical surface 53a and the side surface 43a of the second rotor-side protrusion 43, a third shoe 63 as a third shoe having a hemispherical shape is disposed. The third shoe 63 has a slidable contact surface 63b that is in plane contact with the side surface 43a of the second rotor-side protrusion 43, and a slidable contact surface 63a that is spherically received by the third holding spherical surface 53a. Therefore, the second rotor side protrusion 43 and the second swash plate side protrusion 46 are slidably contacted and engaged via the third shoe 63.

  When the compressor increases the discharge capacity, the swash plate 18 is rotated in the clockwise direction of FIG. 1 and the first shoe 61 is separated from the drive shaft 16 on the cam surface 47a of the cam portion 47 at the same time. As a result, the hinge mechanism 19 guides the movement in which the inclination angle of the swash plate 18 increases. On the contrary, when the compressor reduces the discharge capacity, the swash plate 18 is rotated counterclockwise in FIG. 1 and at the same time, the first shoe 61 moves on the cam surface 47a of the cam portion 47 on the drive shaft 16. The hinge mechanism 19 guides the movement in which the inclination angle of the swash plate 18 is decreased.

  As described above, when the compressor changes the discharge capacity, the first shoe 61 is slid with respect to the cam surface 47a as the first guide plane and is also moved with respect to the second swash plate side protrusion 46. Relative rotation. Therefore, the surface contact between the sliding contact surface 61b of the first shoe 61 and the cam surface 47a of the cam portion 47 is maintained, and the contact between the sliding contact spherical surface 61a of the first shoe 61 and the first holding spherical surface 51a is maintained. Surface contact is also maintained. The cam surface 47a of the cam portion 47 guides the relative movement of the tip of the projection 44 accompanying the tilt of the swash plate 18 corresponding to the change of the discharge capacity.

  Further, when the compressor changes the discharge capacity, the second shoe 62 is slid relative to the side surface 42a of the first rotor side protrusion 42 as the second guide plane, so that the relative movement of the protrusion 44 is achieved. Between the side surface 45a of the first swash plate side protrusion 45 and the sliding contact spherical surface 62a of the second shoe 62, and the side surface 42a of the first rotor side protrusion 42 and the sliding contact plane 62b of the second shoe 62. Surface contact between the two is maintained. Similarly, the third shoe 63 is slid relative to the side surface 43a of the second rotor-side protrusion 43 serving as the third guide plane, so that the relative movement of the protrusion 44 is guided and the second swash plate is used. The surface contact between the side surface 46a of the side projection 46 and the sliding contact spherical surface 63a of the third shoe 63 and between the side surface 43a of the second rotor side projection 43 and the sliding contact plane 63b of the third shoe 63 is maintained.

Therefore, the protrusion 44 is smoothly moved relative to the first and second rotor-side protrusions 42 and 43 and the cam portion 47 when the discharge capacity is changed.
The swash plate 18 may incline in a direction different from the direction in which the discharge capacity is changed due to the biasing action of the axial load caused by the compression reaction force F. More specifically, as shown in FIG. 2, the rotation direction of the drive shaft 16 is the direction of the arrow R, so that the swash plate 18 has a half-circular portion on the compression stroke side, that is, a top dead center corresponding portion TDC and the drive shaft 16. 2 is subjected to a reaction force so as to be pushed forward from the piston 23 due to the compression of the refrigerant gas. Further, the swash plate 18 has a force so that the half-circumference portion on the suction stroke side, that is, the half-circumference portion on the right side in FIG. 2 bordering on the plane H is pulled backward from the piston 23 due to the suction of the refrigerant gas. Receive.

  Therefore, as shown in FIG. 3, the swash plate 18 has side surfaces 45a, 46a of the first and second swash plate side projections 45, 46 that are opposed to the side surfaces of the first and second rotor side projections 42, 43, respectively. It inclines with respect to 42a and 43a, and inclines in the clockwise direction of FIG.2 and FIG.3. Note that FIG. 3 exaggerates the inclination of the swash plate 18 for easy understanding (the first to third shoes 61 to 63 correspond to the exaggerated inclination of the swash plate 18. Shown smaller than actual).

  When the swash plate 18 is inclined in a direction different from the direction in which the discharge capacity is changed, the first shoe 61 is rotated relative to the second swash plate-side protrusion 46 and is relative to the cam surface 47a of the cam portion 47. And slide. Therefore, the surface contact between the sliding contact surface 61b of the first shoe 61 and the cam surface 47a of the cam portion 47 is maintained, and the contact between the sliding contact spherical surface 61a of the first shoe 61 and the first holding spherical surface 51a is maintained. Surface contact is also maintained.

  Similarly, when the swash plate 18 is inclined in a direction different from the direction in which the discharge capacity is changed, the second and third shoes 62 and 63 are respectively in relation to the first and second swash plate side protrusions 45 and 46, respectively. The first and second rotor-side protrusions 42 and 43 are slid relative to the side surfaces 42a and 43a while being relatively rotated. Therefore, the surface contact between the sliding contact planes 62b, 63b of the second and third shoes 62, 63 and the side surfaces 42a, 43a of the first and second rotor side protrusions 42, 43 is maintained, and the second The surface contact between the sliding contact spherical surfaces 62a and 63a of the third shoes 62 and 63 and the second and third holding spherical surfaces 52a and 53a is also maintained.

  As described above, the spherical surface receiving structure of the first to third holding spherical surfaces 51a to 53a of the protrusion 44 and the sliding contact spherical surfaces 61a to 63a of the first to third shoes 61 to 63 is obtained when the discharge capacity is changed. Protrusion due to tilting of the swash plate 18 in a direction different from the direction in which the discharge capacity is changed as well as relative rotation between the projecting portion 44 and the first to third shoes 61 to 63 as the swash plate 18 tilts. 44 and relative rotation of the first to third shoes 61 to 63 are allowed.

In the present embodiment configured as described above, the following operational effects are obtained.
(1) As mentioned above, the 1st-3rd shoes 61-63 are guide planes (side surfaces 42a and 43a, cams) of the 1st hinge part (the 1st and 2nd rotor side projections 42 and 43 and cam part 47). Slidable contact surfaces 61b to 63b that are in plane contact with the surface 47a), and slidable contact surfaces 61a to 63a that are spherically received by the first to third holding spherical surfaces 51a to 53a of the second hinge portion (projection 44). have. Therefore, even when the swash plate 18 is inclined in a direction different from the direction in which the discharge capacity is changed, the first and second rotor-side protrusions 42 and 43 and the cam part 47 and the protrusion 44 are relatively changed when the discharge capacity is changed. Movement can be made smooth. Therefore, the compressor can improve the durability of the hinge mechanism 19 and the capacity controllability is also improved.

  (2) The first holding spherical surface 51a is formed at the tip of the projection 44 (second swash plate side projection 46), and the axial load acting on the swash plate 18 along the axis L of the drive shaft 16 is a cam. It is received by the rotor 17 through the surface 47a, the first shoe 61, and the first holding spherical surface 51a.

  For example, when the angular transmission between the cam portion 47 and the projection 44 occurs in the portion of the hinge mechanism 19 that transmits the axial load, due to the magnitude of the load, the first and second rotor-side projections 42 and 43. In addition, the smooth relative movement between the cam portion 47 and the projection 44 is greatly hindered. Therefore, the first shoe 61 is interposed in the portion, and further, the surface contact between the first shoe 61 and the cam portion 47 and between the first shoe 61 and the projection 44 is caused by the swash plate 18 being discharged capacity. The fact that it can be maintained even in a state tilted in a direction different from the direction in which the first and second rotors are changed is particularly effective in smoothing the relative movement between the first and second rotor-side projections 42 and 43 and the cam portion 47 and the projection 44. .

  (3) The second holding spherical surface 52a is formed on the side surface 45a which is the power transmission surface on the protruding portion 44 side facing the side surface 42a of the first rotor side protrusion 42, and the rotational force of the rotor 17 is The light is transmitted to the swash plate 18 through the side surface 42a of the protrusion 42, the second shoe 62, and the second holding spherical surface 52a.

  For example, the portion of the hinge mechanism 19 that transmits the power hits the corner between the first rotor side protrusion 42 and the protrusion 44 (first swash plate side protrusion 45) due to the magnitude of the transmission power (rotational force T). If this occurs, smooth relative movement between the first and second rotor-side projections 42 and 43 and the cam portion 47 and the projection 44 will be greatly hindered. Accordingly, the second shoe 62 is interposed in the portion, and furthermore, the surface contact between the second shoe 62 and the first rotor-side protrusion 42 and between the second shoe 62 and the protrusion 44 is determined by the swash plate 18. Can be maintained even in a state inclined in a direction different from the direction in which the discharge capacity is changed, particularly in order to make the relative movement between the first and second rotor side projections 42 and 43 and the cam portion 47 and the projection 44 smooth. It becomes effective.

  (4) In the hinge mechanism 19, shoes 61 and 62 are interposed in a portion for transmitting an axial load and a portion for transmitting power, respectively. Further, the hinge mechanism 19 is configured such that the surface contact between the first shoe 61 and the projection 44 and the cam portion 47 and between the second shoe 62 and the projection 44 and the first rotor side projection 42 is the swash plate 18. Is maintained even in a state where it is inclined in a direction different from the direction in which the discharge capacity is changed. Therefore, the first and second rotor-side projections 42 and 43 and the cam portion 47 and the projection 44 are particularly effective for smooth relative movement.

  (5) Of the side surfaces 42a, 43a of the first and second rotor-side projections 42, 43, the side surface 43a of the second rotor-side projection 43 that is not the power transmission side, and the first side that is opposite to the side surface 43a and not the power transmission side The third shoe 63 is also interposed between the side face 46a of the two swash plate side protrusion 46. Furthermore, the hinge mechanism 19 is configured so that the surface contact between the third shoe 63 and the second rotor side protrusion 43 and between the third shoe 63 and the second swash plate side protrusion 46 is reduced. It is configured to be maintained even in a state inclined in a direction different from the direction to be changed. Therefore, the first and second rotor-side projections 42 and 43 and the cam portion 47 and the projection 44 are particularly effective for smooth relative movement.

For example, the following embodiments can also be implemented without departing from the spirit of the present invention.
As shown in FIG. 4, in the side surface 45 a of the first swash plate side protrusion 45, a first surface formed on the base side of the first swash plate side protrusion 45 is a concave surface facing the side surface 42 a of the first rotor side protrusion 42. A fourth shoe seat 54 having a fourth holding spherical surface 54a is formed, and a fourth shoe 64 having a hemispherical shape is disposed between the fourth holding spherical surface 54a and the side surface 42a of the first rotor side protrusion 42. . The fourth shoe 64 has a slidable contact surface 64b that is in plane contact with the side surface 42a of the first rotor-side protrusion 42, and a slidable contact surface 64a that is spherically received by the fourth holding spherical surface 54a.

  Therefore, the rotational force T of the rotor 17 is transmitted to the first swash plate side protrusion 45 not only through the second shoe 62 but also through the fourth shoe 64. Accordingly, since the force received by the second shoe 62 is reduced, the durability of the second shoe 62 can be improved. This leads to an improvement in the durability of the hinge mechanism 19 that makes the relative movement of the first and second rotor-side projections 42 and 43 and the cam portion 47 and the projection 44 smooth.

  Further, a cam portion 48 having a cam surface 48a similar to the cam surface 47a is bulged and formed at the base portion of the first rotor-side protrusion 42 in the engagement groove 41. Then, a fifth shoe seat 55 having a fifth holding spherical surface 55a made of a concave surface facing the cam surface 48a of the cam portion 48 is formed at the tip of the first swash plate side projection 45, and the fifth holding A fifth shoe 65 having a hemispherical shape is disposed between the spherical surface 55a and the cam surface 48a. The fifth shoe 65 includes a slidable contact surface 65b that is in plane contact with the cam surface 48a of the cam portion 48, and a slidable contact surface 65a that is spherically received by the fifth holding spherical surface 55a.

  Therefore, the axial load acting on the swash plate 18 due to the compression reaction force F is received by the rotor 17 through the fifth shoe 65 in addition to the first shoe 61. Accordingly, since the force received by the first shoe 61 is reduced, the durability of the first shoe 61 can be improved. This leads to an improvement in the durability of the hinge mechanism 19 that makes the relative movement of the first and second rotor-side projections 42 and 43 and the cam portion 47 and the projection 44 smooth.

  In the above embodiment, the rotor 17 is provided with the first and second rotor-side projections 42 and 43 as the wall portion and the swash plate 18 is provided with the protrusion 44. A wall portion may be provided on the swash plate 18 while being provided.

  That is, as shown in FIG. 5, first and second swash plate side projections 72 and 73 as wall portions project from the front surface of the swash plate 18 toward the rotor 17. The engaging groove 41 is constituted by the first and second swash plate side protrusions 72 and 73. A protrusion 70 is provided at a position corresponding to the engagement groove 41 on the rear surface of the rotor 17 so as to be inserted between the first and second swash plate side protrusions 72 and 73.

  The first swash plate side protrusion 72 is disposed on the leading side in the rotational direction of the swash plate 18 with respect to the protrusion 70, and the second swash plate side protrusion 73 is disposed on the trailing side. The side surface 70 a on the power transmission side of the protrusion 70 is opposed to the side surface 72 a of the first swash plate side protrusion 72, and the side surface 70 b that is not the power transmission side of the protrusion 70 is on the side surface 73 a of the second swash plate side protrusion 73. Opposed. The cam portion 47 is disposed on the side surface 70 a side at the base portion of the protrusion 70.

  A first shoe seat 74 having a first holding spherical surface 74 a as a first holding spherical surface formed of a convex surface facing the cam surface 47 a of the cam portion 47 is formed at the tip of the first swash plate side protrusion 72. Yes. Between the first holding spherical surface 74a and the cam surface 47a of the cam portion 47, a spherical surface is received by a sliding contact plane 75b and a first holding spherical surface 74a which are in plane contact with the cam surface 47a (first guide plane). A first shoe 75 is disposed as a first shoe having a slidable contact spherical surface 75a.

  On the side surface 72 a of the first swash plate side protrusion 72, a second shoe seat 52 is recessed on the tip side of the first swash plate side protrusion 72. The second shoe 62 is in plane contact with the side surface 70a of the projection 70, which is the second guide plane, with the sliding contact plane 62b, and is received by the second holding spherical surface 52a with the sliding contact spherical surface 62a. A third shoe seat 53 is recessed in the side surface 73 a of the second swash plate side protrusion 73 on the base side of the second swash plate side protrusion 73. The third shoe 63 is in plane contact with the side surface 70b of the projection 70, which is the third guide plane, with the sliding contact plane 63b, and is received by the third holding spherical surface 53a with the sliding contact spherical surface 63a.

Also in this aspect, the same effects as the effects (1) to (5) of the embodiment are obtained.
In the above embodiment, the rotor-side hinge portion is the first hinge portion, and the cam plate-side hinge portion is the second hinge portion. However, the cam plate-side hinge portion is changed to the first hinge portion. And the rotor-side hinge is the second hinge. That is, a guide plane (cam surface) is formed on the cam plate side hinge portion, and a holding spherical surface is formed on the rotor side hinge portion.

The present invention is embodied in a wobble type variable capacity compressor provided with a swing plate as a cam plate.
In the above embodiment, the variable displacement swash plate compressor provided with the single-headed piston 23 is embodied. However, in the variable displacement swash plate compressor provided with the double-headed piston, this is changed. Make it concrete.

The longitudinal cross-sectional view of a capacity variable type compressor. The top view which shows a hinge mechanism. The top view which shows the state which the swash plate inclined in the direction different from the direction which changes discharge capacity. The top view which shows the hinge mechanism in another example. The top view which shows the hinge mechanism in another example. The fragmentary sectional view which shows the hinge mechanism in background art. The top view which similarly shows a hinge mechanism.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 11 ... Cylinder block, 12 ... Front housing, 14 ... Rear housing (11, 12, 14 comprises a housing), 16 ... Drive shaft, 17 ... Rotor, 18 ... Swash plate as a cam plate, 19 ... Hinge mechanism, 23 ... piston, 42, 43 ... first and second rotor-side projections (42a ... second guide plane and side surface as power transmission surface) constituting the rotor-side hinge portion and the first hinge portion, 43a ... side surfaces as third guide planes), 44 ... projections as cam plate side hinges and second hinge parts (45a ... sides as power transmission surfaces, 46a ... sides), 47 ... rotor side hinges and first 1 cam portion (47a... Cam surface as a first guide plane), 51a... First holding spherical surface as a first holding spherical surface, 52a... As a second holding spherical surface. 2 holding spherical surfaces, 53a ... third holding spherical surface as third holding spherical surface, 61 ... first shoe as first shoe (61a ... sliding contact spherical surface, 61b ... sliding contact plane), 62 ... as second shoe Second shoe (62a ... sliding contact spherical surface, 62b ... sliding contact plane), 63 ... third shoe as a third shoe (63a ... sliding contact spherical surface, 63b ... sliding contact plane), 70 ... rotor side hinge portion and Projections (70a: second guide plane and side as power transmission surface, 70b: side as third guide plane) constituting the first hinge part, 72, 73 ... cam plate side hinge part, second hinge First and second swash plate side protrusions (72a: side surface as a power transmission surface, 73a ... side surface), 74a: first holding spherical surface as a first holding spherical surface, 75 ... first shoe As a first shoe (75a ... sliding contact spherical surface, 7 b ... sliding plane), L ... axis, T ... rotational force.

Claims (6)

A drive shaft is rotatably supported on the housing, and a rotor is provided on the drive shaft so as to be integrally rotatable. A cam plate is slidably and tiltably supported on the drive shaft. The rotor and the cam plate A hinge mechanism is interposed between the rotor side hinge portion, the rotor side hinge portion provided on the rotor, and the cam plate. The hinge mechanism is slidably contacted with the rotor side hinge portion via a shoe. The rotary motion of the drive shaft is converted into the reciprocating motion of the piston through the rotor, the hinge mechanism and the cam plate, and the compression of the gas is performed. In the variable displacement compressor capable of changing the discharge capacity by sliding the cam plate while tilting on the drive shaft by the guide of the hinge mechanism ,
The first hinge part, which is one of the rotor side hinge part and the cam plate side hinge part, is formed with a guide plane for guiding the relative movement of the other second hinge part, and the second hinge part. A holding spherical surface is formed opposite to the guide plane, and the shoe is in sliding contact with the guide plane of the first hinge portion and the holding portion of the second hinge portion. A variable capacity compressor having a sliding contact spherical surface received by a spherical surface.   The second hinge part has a projecting shape, and the first hinge part has a cam surface for guiding relative movement of the tip of the second hinge part as the cam plate is tilted when the discharge capacity is changed. The cam surface forms the guide plane, the holding spherical surface is formed at the tip of the second hinge portion, and the axial load acting on the cam plate along the axis of the drive shaft is: The variable capacity compressor according to claim 1, wherein the compressor is received by the rotor through the guide plane, the shoe, and the holding spherical surface.   A power transmission surface that transmits power to and from the second hinge portion is formed on the first hinge portion, the power transmission surface forms the guide plane, and the holding spherical surface faces the guide plane. The power transmission surface on the second hinge portion side is formed, and the rotational force of the rotor is transmitted to the cam plate via the guide plane, the shoe, and the holding spherical surface. Variable capacity compressor.   One of the rotor side hinge portion and the cam plate side hinge portion includes two wall portions, and the other of the rotor side hinge portion and the cam plate side hinge portion is inserted between the two wall portions. Of the side surfaces of the first hinge portion that face the side surfaces of the second hinge portion, the side surface that is not the power transmission side forms the guide plane, and the holding spherical surface is the second hinge portion. The variable capacity compressor according to claim 1, wherein the compressor is formed on a side surface that is opposed to the guide plane and is not on a power transmission side. The second hinge part has a projecting shape, and the first hinge part is a cam that guides relative movement of the tip of the second hinge part as the cam plate tilts in response to a change in discharge capacity. A surface is formed, the cam surface forms the first guide plane, and the first holding spherical surface is formed at the tip of the second hinge portion, and is formed on the cam plate along the axis of the drive shaft. The acting axial load is received by the rotor via the first guide plane, the first shoe and the first holding spherical surface,
A power transmission surface that transmits power to and from the second hinge portion is formed on the first hinge portion, the power transmission surface forms the second guide plane, and the second holding spherical surface is It is formed on the power transmission surface on the second hinge portion side facing the second guide plane, and the rotational force of the rotor is such that the second guide plane, the second shoe, and the second holding The variable capacity compressor according to claim 1, wherein the variable capacity compressor is transmitted to the cam plate via a spherical surface.   One of the rotor side hinge portion and the cam plate side hinge portion includes two wall portions, and the other of the rotor side hinge portion and the cam plate side hinge portion is inserted between the two wall portions. Of the side surfaces of the first hinge portion that face the side surfaces of the second hinge portion, the side surface that is not on the power transmission side forms the third guide plane, and the third holding spherical surface. Is formed on a side surface of the second hinge portion that faces the third guide plane and that is not on the power transmission side, and a third gap is formed between the third guide plane and the third holding spherical surface. The variable capacity compressor according to claim 5, wherein the shoe is interposed.

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