JP6063150B2 - Variable capacity compressor - Google Patents

Description

  The present invention relates to a variable capacity compressor, and more particularly to a variable capacity compressor used in a vehicle air conditioner system.

  Patent Document 1 discloses a hinge mechanism (link mechanism) that connects two components so as to be rotatable by a connection pin. Patent Document 2 discloses a technique for adding a relative movement restricting means to stabilize the behavior of the swash plate relative to the drive shaft.

JP 2003-172333 A JP 2002-364530 A

  In the hinge mechanism (link mechanism) described in Patent Document 1, when the swash plate is tilted in the left-right direction by the action of the axial load caused by the compressive load, the through hole of the swash plate is tilted and the through hole is the outer periphery of the drive shaft. There is a problem that the contact portion is worn by the edge contact with the surface, and the swash plate cannot be smoothly tilted. In particular, the compression load increases on the maximum inclination side of the swash plate, so that the wear progresses quickly and the tilt of the swash plate is hindered.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a variable capacity compressor in which wear of a contact portion between a through hole of a swash plate and an outer peripheral surface of a drive shaft is suppressed, and the swash plate can be smoothly tilted.

In order to solve the above problems, a variable displacement compressor according to the present invention includes a housing in which a discharge chamber, a suction chamber, a crank chamber and a cylinder bore are formed, a piston disposed in the cylinder bore, and the housing A drive shaft that is rotatably supported by the motor, a rotor that rotates integrally with the drive shaft, a swash plate that rotates in synchronization with the rotation of the rotor connected via a connecting means, and the rotation of the swash plate. A conversion mechanism that converts the reciprocating motion of the piston, and a pressure control valve that can control the internal pressure of the crank chamber according to the opening,
When the opening degree is changed and the internal pressure of the crank chamber is changed, the inclination of the swash plate with respect to the drive shaft is changed while the swash plate is slid with the drive shaft to change the stroke of the piston. A variable capacity compressor configured to be capable of changing a discharge capacity when compressing the refrigerant sucked into the cylinder bore from the suction chamber and discharging the refrigerant into the discharge chamber,
The compression process side region closer to the positive direction of rotation of the swash plate than the suction process side region closer to the negative direction of rotation of the swash plate as viewed from the portion corresponding to the top dead center position of the piston on the swash plate The swash plate is inclined and connected to the rotor so as to move away from a receiving surface of a thrust bearing formed on the rotor ,
The connecting means includes a first arm protruding from the rotor, a second arm protruding from the swash plate, and one end side rotatably connected to the first arm via a first connecting pin. The other end side comprises a link mechanism including a link arm rotatably connected to the second arm via a second connection pin,
A plane including the top dead center position and the bottom dead center position of the swash plate while being orthogonal to the annular plane portion of the swash plate is defined as a plane U, and a plane orthogonal to the plane U while being orthogonal to the annular plane portion. When the plane is V and the swash plate is divided into the compression process side and the suction process side on the plane U, one end of the second connecting pin on the compression process side approaches the plane V, and the first connection pin is on the suction process side. The second connecting pin is inclined at a predetermined angle with respect to the plane V so that the other end of the two connecting pins is away from the plane V.

  According to such a variable capacity compressor according to the present invention, when a compressive load is applied to the swash plate by the operation of the variable capacity compressor, the contact between the through hole and the outer peripheral surface of the drive shaft becomes close to a line contact, As a result, wear of the contact portion between the through hole and the outer peripheral surface of the drive shaft is suppressed, and the swash plate can be tilted smoothly.

  Further, when the tilt angle is maximized, the thrust bearing receiving surface of the swash plate is more in the compression process side region than the suction process side region of the swash plate, as viewed from the portion corresponding to the top dead center position. It is preferable that the degree of moving away from is maximized. According to such a configuration, when the inclination angle of the swash plate is the maximum inclination angle, the compression load becomes maximum, and the compression load decreases as the inclination angle decreases from the maximum inclination angle. In actual operation, the contact between the through hole and the outer peripheral surface of the drive shaft becomes close to a line contact.

  Further, when the inclination angle is minimized, the thrust bearing receiving surface of the swash plate is more compact than the suction process side region of the swash plate when viewed from the portion corresponding to the top dead center position. It is preferable that the degree of moving away from the position is minimized, and the minimum value of the tilt angle is set to approximately 0 °. Since the compressive load hardly acts when the minimum inclination angle is approximately 0 °, it is possible to avoid unnecessarily inclining the swash plate.

  ADVANTAGE OF THE INVENTION According to this invention, the variable capacity compressor which implement | achieved smooth tilting of the swash plate with a simple structure can be provided.

It is a longitudinal section showing a variable capacity compressor concerning one embodiment of the present invention. It is a figure which shows the link arm of FIG. 1, (a) is a top view, (b) is the arrow view seen from the A direction of (a). It is a perspective view which shows the coupling body of the drive shaft and rotor of FIG. It is a perspective view which shows the swash plate of FIG. It is a front view which shows the coupling body of the drive shaft of FIG. 1, a rotor, a link arm, and a swash plate. It is the top view which looked at the swash plate of FIG. 1 from the rotor side. FIG. 7 is a partial plan view showing a connection body of a second connection pin and a swash plate of FIG. 6. The positional relationship between the rotor, the drive shaft, the link arm, and the swash plate is shown. It is. With respect to the swash plate of FIG. 1, (a) shows a state where the tilt angle is maximum, and (b) shows a state where the tilt angle is minimum. For each of (a) and (b), the upper left figure is an arrow view seen from the C2 and C1 directions, the upper right figure is an arrow view seen from the B2 and B1 directions, and the lower figure is a side view. It is a model side view for demonstrating the inclination of a swash plate at the time of operation | movement of the variable capacity compressor of FIG. FIG. 9 is a partially enlarged schematic cross-sectional view in which a contact portion between the swash plate and the drive shaft in FIG. 8 is enlarged. It is the top view which looked at the swash plate of the variable capacity compressor which concerns on the other embodiment of this invention from the rotor side.

The variable capacity compressor according to the present invention can be explained as follows when it is explained through a virtual plane (planes P1 to P3) so as to be visually easy to understand. That is, the variable capacity compressor according to the present invention includes a housing having a discharge chamber, a suction chamber, a crank chamber, and a cylinder bore formed therein, a piston disposed in the cylinder bore, and a rotatably supported in the housing. A drive shaft, a rotor fixed to the drive shaft and rotating integrally with the drive shaft, and the rotor connected to the rotor via a connecting means, and rotated in synchronization with the rotor and inclined with respect to the axis of the drive shaft A swash plate slidably attached to the drive shaft through a through-hole through which the drive shaft is inserted, and a conversion mechanism that converts the rotation of the swash plate into a reciprocating motion of the piston. A control valve for adjusting the pressure in the crank chamber, changing the pressure in the crank chamber by adjusting the opening of the control valve, changing the tilt angle of the swash plate, adjusting the stroke of the piston, and The variable displacement compressor which discharges into the discharge chamber from the chamber to compress the sucked refrigerant in the cylinder bore,
The plane defined by the axis of the drive shaft and the top dead center position of the swash plate is P1, the annular plane of the swash plate is P2, and the plane that intersects the plane P1 and the plane P2 is orthogonal to the plane P1. P3, and when the swash plate is divided into a compression process side region and a suction process side region on the plane P1, the drive shaft, the rotor, the connecting means and the swash plate connection body The plane P2 is in relation to the plane P3 so that the outermost part of the plane P2 in the region is farther from the receiving surface of the thrust bearing formed on the rotor than the outermost side of the plane P2 in the region on the suction process side that is a symmetrical position. And is inclined at a predetermined angle.

  According to such a variable capacity compressor according to the present invention, when a compressive load is applied to the swash plate by the operation of the variable capacity compressor, the contact between the through hole and the outer peripheral surface of the drive shaft becomes close to a line contact, As a result, wear of the contact portion between the through hole and the outer peripheral surface of the drive shaft is suppressed, and the swash plate can be tilted smoothly.

  The predetermined angle is preferably the largest at the maximum inclination angle of the swash plate and decreases as the inclination angle decreases from the maximum inclination angle. According to such a configuration, when the inclination angle of the swash plate is the maximum inclination angle, the compression load becomes maximum, and the compression load decreases as the inclination angle decreases from the maximum inclination angle. In actual operation, the contact between the through hole and the outer peripheral surface of the drive shaft becomes close to a line contact.

  The minimum inclination angle of the swash plate is preferably set to approximately 0 °, and the predetermined angle is preferably approximately 0 ° as the minimum inclination angle. Since the compressive load hardly acts at the minimum tilt angle of approximately 0 °, it is possible to avoid unnecessarily tilting the swash plate.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.

(1) Variable displacement compressor A variable displacement compressor 100 shown in FIG. 1 is a clutchless compressor, and includes a cylinder block 101 having a plurality of cylinder bores 101a, and a front housing 102 provided at one end of the cylinder block 101. A cylinder head 104 is provided at the other end of the cylinder block 101 via a valve plate 103.

  A drive shaft 110 is provided across the inside of the crank chamber 140 defined by the cylinder block 101 and the front housing 102, and a swash plate 111 is disposed around an intermediate portion thereof. A through hole 111a through which the drive shaft 110 is inserted is formed in the swash plate 111. The through hole 111a has an inclination angle of the swash plate perpendicular to the annular plane of the swash plate 111, and the top dead center position of the swash plate and the drive shaft. The shape is formed so as to be tiltable in the range of the maximum inclination angle and the minimum inclination angle about the pivot axis K orthogonal to the plane including The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120, and the inclination angle θ can be changed while the side surface of the through hole 111 a is slidably supported on the outer peripheral surface of the drive shaft 110. Yes.

  The through hole 111a is formed with a minimum inclination angle restricting portion that comes into contact with the drive shaft 110. In the embodiment, when the annular plane of the swash plate 111 is orthogonal to the drive shaft 110, When the tilt angle is 0 °, the minimum tilt angle restricting portion of the through hole 111a is formed so that the tilt angle θ of the swash plate is approximately 0 °. The minimum tilt angle of approximately 0 ° means that the minimum tilt angle is greater than −0.5 ° and less than 0.5 °, but preferably the minimum tilt angle is set to 0 ° or more and less than 0.5 °. The

  Between the rotor 112 and the swash plate 111, an inclination reducing spring 114 made of a compression coil spring that urges the swash plate 111 to the minimum inclination angle is mounted, and between the swash plate 111 and the spring support member 116, there is an inclination. A tilt-increasing spring 115 made up of a compression coil spring that urges the plate 111 in a direction to increase the tilt angle to a predetermined tilt angle smaller than the maximum tilt angle is mounted. Since the biasing force of the tilt increasing spring 115 is set to be larger than the biasing force of the tilt decreasing spring 114 at the minimum tilt angle, when the drive shaft 110 is not rotating, the biasing force of the tilt decreasing spring 114 and the tilt increasing spring 115 are increased. The swash plate 111 is positioned so as to form a predetermined tilt angle at which the resultant force with the urging force becomes zero.

  One end of the drive shaft 110 extends through the inside of the boss portion 102a protruding to the outside of the front housing 102, and is connected to a power transmission device (not shown). A shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102a to shut off the inside and the outside. The drive shaft 110 and the rotor 112 are supported by bearings 131 and 132 in the radial direction, and supported by the bearing 133 and the thrust plate 134 in the thrust direction. Power from an external drive source is transmitted to the power transmission device, and the drive shaft 110 is driven. Is rotatable in synchronization with the rotation of the power transmission device. The gap between the contact portion of the drive shaft 110 with the thrust plate 134 and the thrust plate 134 is adjusted to a predetermined distance by the adjusting screw 135.

  A piston 136 is disposed in the cylinder bore 101 a, and the outer space of the swash plate 111 is accommodated in the inner space of the end of the piston 136 protruding to the crank chamber 140 side. The piston 136 is linked to the structure. Therefore, the piston 136 can reciprocate in the cylinder bore 101a by the rotation of the swash plate 111.

  In the cylinder head 104, a suction chamber 141 and a discharge chamber 142 surrounding the radially outer portion of the suction chamber 141 in an annular shape are defined on the center side. The suction chamber 141 communicates with the cylinder bore 101a through a communication hole 103a provided in the valve plate 103 and a suction valve (not shown). The discharge chamber 142 communicates with the cylinder bore 101 a through a discharge valve (not shown) and a communication hole 103 b provided in the valve plate 103.

  The front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 105 through a gasket (not shown) to form a compressor housing.

  Further, in FIG. 1, a muffler is provided on the upper portion of the cylinder block 101, and the muffler is fastened by a bolt with a lid member 106 and a forming wall 101b formed on the upper portion of the cylinder block 101 via a seal member (not shown). It is formed by. A check valve 200 is disposed in the muffler space 143. The check valve 200 is disposed at a connection portion between the communication path 144 and the muffler space 143 and operates in response to a pressure difference between the communication path 144 (upstream side) and the muffler space 143 (downstream side). When the pressure difference is smaller than the predetermined value, the communication path 144 is shut off, and when the pressure difference is larger than the predetermined value, the communication path 144 is opened. Thus, the discharge chamber 142 is connected to the discharge-side refrigerant circuit of the air conditioner system via the discharge passage formed by the communication passage 144, the check valve 200, the muffler space 143, and the discharge port 106a.

The cylinder head 104 is formed with a suction port 104a and a communication passage 104b, and the suction chamber 141 is connected to a suction side refrigerant circuit of the air conditioner system through a suction passage formed by the communication passage 104b and the suction port 104a. . The suction passage extends linearly from the radially outer side of the cylinder head 104 so as to cross a part of the discharge chamber 142.

  The cylinder head 104 is further provided with a control valve 300. The control valve 300 controls the amount of discharge gas introduced into the crank chamber 140 by adjusting the opening of the communication passage 145 that communicates the discharge chamber 142 and the crank chamber 140. The refrigerant in the crank chamber 140 flows to the suction chamber 141 via the communication passage 101 c, the space 146, and the orifice 103 c formed in the valve plate 103.

  Therefore, it is possible to variably control the discharge capacity of the variable capacity compressor 100 by changing the pressure of the crank chamber 140 by the control valve 300 and changing the inclination angle of the swash plate 111 (that is, changing the stroke of the piston 136). it can.

  When the air conditioner is activated (that is, when the variable capacity compressor 100 is in an activated state), the energization amount to the solenoid built in the control valve 300 is adjusted based on the external signal, and the pressure in the suction chamber 141 is set to a predetermined value. The discharge capacity is variably controlled so that The control valve 300 can optimally control the suction pressure according to the external environment.

  Further, when the air conditioner is not operated (that is, when the variable capacity compressor 100 is in the non-operating state), the communication passage 145 is forcibly opened by turning off the energization to the solenoid built in the control valve 300 to be variable. The discharge capacity of the capacity compressor 100 can be controlled to the minimum.

(2) Link mechanism A rotor 112 is fixed to the drive shaft 110, and a pair of first arms 112a are projected from the rotor 112. One end side 121a of the link arm 121 formed in a substantially cylindrical shape is guided inside the pair of first arms 112a. Further, by inserting a first connecting pin 122 as a connecting means into a through hole 112b formed in the first arm 112a and a through hole 121b formed in one end side 121a of the link arm 121, a link is established. The arm 121 is rotatable around the axis of the first connecting pin 122 while being guided by the pair of first arms 112a.

  The first connecting pin 122 is press-fitted and held in a through hole 121b formed in the link arm 121, and a small gap is formed between the outer periphery of the first connecting pin 122 and the through hole 112b formed in the first arm 112a. Is formed.

  The other end 121c of the link arm 121 is a pair of arms projecting from one end side 121a formed in a cylindrical shape, and a second arm 111b projecting from the swash plate 111 is guided inside thereof. The By inserting a second connecting pin 123 as a connecting means into a through hole 121d formed in the other end side 121c of the link arm 121 and a through hole 111c formed in the second arm 111b, the link arm is inserted. 121 and the swash plate 111 are connected, and the link arm 121 and the swash plate 111 are relatively rotatable about the axis of the second connecting pin 123. The second connecting pin 123 is press-fitted and held in the through hole 111c of the second arm 111b, and a minute gap is formed between the outer periphery of the second connecting pin 123 and the through hole 121d formed in the link arm 121. ing.

  A link mechanism 120 is configured by the first arm 112 a, the second arm 111 b, the link arm 121, the first connection pin 122, and the second connection pin 123. Accordingly, the swash plate 111 is connected to the rotor 112 fixed to the drive shaft 110 via the link mechanism 120, rotates by receiving the rotational torque of the rotor 112, and the inclination angle can be changed along the drive shaft 110. It has become.

(3) Second connecting pin (inclined arrangement)
FIG. 5 shows a state in which the connecting body of the drive shaft 110, the rotor 112, the link mechanism 120, and the swash plate 111 is viewed from the direction facing the link mechanism 120.

  A line segment indicated by P1 is a plane P1 defined by the axis of the drive shaft 110 and the top dead center position (and bottom dead center position) of the swash plate, and this plane P1 corresponds to the cross section of FIG. The top dead center position of the swash plate refers to a position where the compression process of the piston 136 ends, and the bottom dead center position refers to a position where the suction process of the piston 136 ends. P2 is an annular plane P2 of the swash plate 111, and P3 includes a plane P3 that includes an intersection line G (a line segment from the front side to the back in the drawing) of the plane P1 and the plane P2 and is orthogonal to the plane P1. Point to. When the swash plate 111 is divided into a compression process side area and a suction process side area on the plane P1, the right side in the figure is the compression process side and the left side in the figure is the suction process side.

  In the present embodiment, since there are two annular planes P2 of the swash plate 111, one of them may be determined as P2.

  FIG. 6 shows a state in which the swash plate 111 is viewed from the rotor 112 side. In the figure, U is a plane U that is orthogonal to the annular plane P2 of the swash plate 111 and includes the top dead center position of the swash plate and the centers of both side surfaces of the through hole 111a, V is orthogonal to the plane P2, and The plane V includes the pivot axis K of the swash plate orthogonal to the plane U. A state in which the intersecting line of the plane U and the plane V coincides with the axis of the drive shaft 110 is a state where the swash plate has an inclination angle of 0 °. In the plane U, the upper side in the drawing coincides with the top dead center position of the swash plate, and the lower side coincides with the bottom dead center position of the swash plate, and substantially coincides with the plane P1. The center of the second arm 111b coincides with the plane U.

  As shown in FIG. 6, the axis m along the axial direction of the through hole 111c of the second arm 111b is an intersection on the plane U with respect to the axis n orthogonal to the plane U and intersecting the axis m on the plane U. Here, the axis n is processed so as to be inclined at an angle α to the center. The axis n is an axis along the axial direction of the through hole 111c when not inclined to the angle α. Therefore, as shown in FIG. 7, the second connecting pin 123 press-fitted and fixed in the through hole 111c is inclined by an angle α so that the right end in the drawing approaches the plane V and the left end moves away from the plane V. doing. Although the angle α is exaggerated in FIGS. 5 and 7, it is actually a small angle of less than 0.5 °, for example. The angle α is set in the range of 0.2 ° to 1 °, preferably 0.2 ° to 0.5 °.

  Since the second connecting pin 123 is parallel to the plane P2 when the tilt angle of the swash plate is 0 °, the plane P2 coincides with the plane P3 as shown in FIG. 5 when the tilt angle is 0 °. That is, the annular plane P2 of the swash plate 111 is orthogonal to the plane P1.

(4) Swash plate through hole (offset)
Both ends of the second connecting pin 123 are inserted into and supported by the through-hole 121d of the link arm 121, but the through-hole 121d of the link arm 121 is parallel to the axis n shown in FIG. It is parallel to the axis line along the axial direction of the hole 121b and the through-hole 112b of the first arm.

  When the drive shaft 110, the rotor 112, the link mechanism 120, and the swash plate 111 are combined into one connecting body, if the second connecting pin 123 is inclined, the second connecting pin 123 is restrained by the through hole 121d. Therefore, the swash plate 111 rotates counterclockwise in FIG. 6 around the intersection of the axis m and the axis n within the gap between the through hole 111a of the swash plate and the outer peripheral surface of the drive shaft 110, and as a result. The side surface of the through hole 111 a on the suction process side contacts the outer peripheral surface of the drive shaft 110.

  When the outer peripheral surface of the drive shaft 110 comes into contact with the side surface of the through-hole 111a on the suction process side, the inclination of the swash plate 111 increases when a compression load is applied, and the distance between the application point of the compression load and the contact point is the compression process side. There is a concern that the swash plate 111 may not be smoothly tilted in the direction of deformation due to the frictional force.

  Therefore, as shown in FIG. 8, the axis of the drive shaft 110 is offset by ΔL from the center of both side surfaces of the through hole 111a.

  FIG. 8A shows the connecting body of the drive shaft 110 and the rotor 112 as viewed from the swash plate 111 side, and T includes the axis of the drive shaft 110 and the inner surface of the first arm 112a (one end side 121a of the link arm). Is a plane T parallel to the guide surface).

  The pair of first arms 112a of the rotor 112 is arranged in parallel to the plane T, and the distance L1 between the guide surface on the one end 121a side of the link arm in the first arm 112a1 on the left side in the drawing and the plane T is the first arm 112a2. The distance L2 between the guide surface on the one end 121a side of the link arm and the plane T is slightly larger. That is, the guide surfaces of the pair of first arms 112a are not symmetrically arranged with respect to the plane T, and the center of the pair of first arms 112a is ΔL = (L1−L2) / Offset by two. In addition, although ΔL is exaggerated in the drawing, it is actually a very small value of 0.2 mm or less, for example.

  8B, the two guide surfaces of the second arm 111b of the pair of arms 121c on both ends (contact portions) on the one end 121a side of the link arm 121 and the center of the link arm 121 are left and right. Therefore, the center of the link arm 121 is coincident with the plane U shown in FIG. 8C.

  Therefore, the plane T is offset by ΔL in the left direction in the drawing with respect to the center of both side surfaces of the through hole 111a. Thus, even when the second connecting pin 123 is inclined, the side surface on the compression process side of the through hole 111c. Is in contact with the outer peripheral surface of the drive shaft 110.

(5) Tilt of the annular plane of the swash plate FIG. 9 shows how the plane P2 tilts with respect to the plane P3 when the tilt angle of the swash plate changes. FIG. 9A shows a state where the inclination angle of the swash plate is the maximum inclination angle, and FIG. 9B shows a state where the inclination angle of the swash plate is the minimum inclination angle. In addition, the state which looked at the 2nd connection pin 123 and the swash plate 111 from the direction of the arrow above the connection body of the drive shaft 110, the rotor 112, the link mechanism 120, and the swash plate 111 was shown typically.

  When the inclination angle of the swash plate is 0 °, the second connecting pin 123 is parallel to the plane P2 as shown in the upper left figure of FIG. 9B. Therefore, as shown in the upper right figure of FIG. Coincides with the plane P3. That is, the annular plane P2 of the swash plate is orthogonal to the plane P1.

  When the inclination angle of the swash plate increases and reaches the maximum inclination angle, the second connecting pin 123 is inclined as shown in FIG. 7, so that the second connecting pin 123 is shown in FIG. 7, the left end (inhalation process side) tends to move away from the reference plane R of the rotor, and the right end (compression process side) tends to move in a direction approaching the reference plane R of the rotor. Note that the reference surface R of the rotor is a receiving surface of the bearing 133.

  However, since both ends of the second connection pin 123 are restrained by the through-hole 121d of the link arm, the second connection pin 123 itself exceeds the range of the gap between the second connection pin 123 and the through-hole 121d. As a result, the swash plate 111 tilts in the direction opposite to the tilt direction of the second connecting pin 123 as shown in the upper right view of FIG.

  That is, the annular plane P2 of the swash plate moves in the direction in which the outermost part on the compression process side is furthest away from the reference plane R of the rotor, and the outermost part on the suction process side moves in the direction closest to the reference plane R of the rotor. Is inclined by an angle β with respect to the plane P3. Therefore, the angle formed by the plane P2 and the plane P3 is zero when the tilt angle of the swash plate is 0 °, and increases as the tilt angle increases, and becomes the maximum angle β at the maximum tilt angle.

  When the variable capacity compressor 100 is operated and the piston 136 compresses the gas, the compression load acts on the swash plate 111 via the piston 136.

  In the no-load state with no compression load, the plane P2 is inclined with respect to the plane P3, and the surface on the compression process side is away from the reference plane of the rotor. However, when the piston 136 compresses the gas, the compression load acts. The swash plate 111 is tilted so that the plane P2 of the swash plate approaches the plane P3. Since the compressive load increases under a load condition in which the swash plate is operated at the maximum inclination angle, as shown in FIG. 10, the plane P2 of the swash plate when operated in the vicinity of the maximum inclination almost coincides with the plane P3. As shown, the angle β and thus the angle α are set.

  Thereby, when the variable capacity compressor 100 is operated under a load condition with a large compressive load, the plane P2 substantially coincides with the plane P3, so that the inclination of the through hole 111a is suppressed as shown in FIG. Contact between the side surface on the compression process side and the outer peripheral surface of the drive shaft 110 is close to line contact. As a result, wear of the contact portion between the through hole 111a and the outer peripheral surface of the drive shaft 110 is suppressed, and the tilting of the swash plate 111 becomes smooth.

  In the no-load state, the plane P2 is inclined with respect to the plane P3. However, the inclination of the swash plate decreases as the inclination angle of the swash plate decreases, and the compression load decreases as the inclination angle of the swash plate decreases. The plane P2 when actually operating regardless of the inclination angle approaches the plane P3. Therefore, regardless of the inclination angle of the swash plate, the contact between the side surface of the through hole 111a on the compression process side and the outer peripheral surface of the drive shaft 110 is close to a line contact, and the contact portion between the through hole 111a and the outer peripheral surface of the drive shaft 110 Wear is suppressed and tilting of the swash plate becomes smooth.

  In the above-described embodiment, the link mechanism is exemplified as the connecting means, but other hinge mechanisms (for example, as shown in Patent Document 2) may be used.

  In the embodiment described above, the first arm of the rotor is offset, but the link arm or the second arm of the swash plate may be offset.

  In the above-described embodiment, the second connecting pin is inclined with respect to the second arm by the angle α. However, the second arm is directed toward the region on the compression process side with respect to the plane U as shown in FIG. The axis α of the second connecting pin may be inclined by the angle α, and the axis m of the second connecting pin may be inclined by the angle α with respect to the axis n (in this case, the second connecting pin is arranged orthogonal to the second arm). .)

  Furthermore, although the clutchless compressor is exemplified in the above-described embodiment, the present invention is also applied to a variable displacement compressor equipped with an electromagnetic clutch, a swing plate type variable displacement compressor, and a variable displacement compressor driven by a motor. The invention can be applied.

  The present invention can be used as a variable capacity compressor for a vehicle air conditioner system or the like.

DESCRIPTION OF SYMBOLS 100 Compressor 101 Cylinder block 101a Cylinder bore 101b Formation wall 101c Communication path 102 Front housing 102a Boss part 103 Valve plate 103a, 103b Communication hole 103c Orifice 104 Cylinder head 104a Suction port 104b Communication path 105 Through bolt 106 Lid member 106a Discharge port 110 Drive Shaft 111 Swash plate 111a Through hole 111b Second arm 111c Through hole 112 Rotor 112a, 112a1, 112a2 First arm 112b Through hole 114 Inclination decreasing spring 115 Inclination increasing spring 116 Spring support member 120 Link mechanism 121 Link arm 121a One end of link arm 121b Through hole 121c Other end 121d of link arm Through hole 122 First connecting pin 123 Second connecting pin 130 Shaft seal device 131, 32, 133 Bearing 134 Thrust plate 135 Adjustment screw 136 Piston 137 Shoe 140 Crank chamber 141 Suction chamber 142 Discharge chamber 143 Muffler space 144, 145 Communication path 146 Space 200 Check valve 300 Control valve K Axis P1, P2, P3, T, U, V plane

Claims (3)

A housing having a discharge chamber, a suction chamber, a crank chamber, and a cylinder bore formed therein, a piston disposed in the cylinder bore, a drive shaft rotatably supported by the housing, and a rotation integrally with the drive shaft And a swash plate that rotates in synchronization with the rotation of the rotor connected via connecting means, a conversion mechanism that converts the rotation of the swash plate into a reciprocating motion of the piston, and the crank according to the opening degree. A pressure control valve capable of controlling the internal pressure of the chamber,
When the opening degree is changed and the internal pressure of the crank chamber is changed, the inclination of the swash plate with respect to the drive shaft is changed while the swash plate is slid with the drive shaft to change the stroke of the piston. A variable capacity compressor configured to be capable of changing a discharge capacity when compressing the refrigerant sucked into the cylinder bore from the suction chamber and discharging the refrigerant into the discharge chamber,
The compression process side region closer to the positive direction of rotation of the swash plate than the suction process side region closer to the negative direction of rotation of the swash plate as viewed from the portion corresponding to the top dead center position of the piston on the swash plate The swash plate is inclined and connected to the rotor so as to move away from a receiving surface of a thrust bearing formed on the rotor ,
The connecting means includes a first arm protruding from the rotor, a second arm protruding from the swash plate, and one end side rotatably connected to the first arm via a first connecting pin. The other end side comprises a link mechanism including a link arm rotatably connected to the second arm via a second connection pin,
A plane including the top dead center position and the bottom dead center position of the swash plate while being orthogonal to the annular plane portion of the swash plate is defined as a plane U, and a plane orthogonal to the plane U while being orthogonal to the annular plane portion. When the plane is V and the swash plate is divided into the compression process side and the suction process side on the plane U, one end of the second connecting pin on the compression process side approaches the plane V, and the first connection pin is on the suction process side. The variable capacity compressor , wherein the second connecting pin is inclined at a predetermined angle with respect to the plane V so that the other end of the two connecting pins is away from the plane V.   When the tilt angle is maximized, the compression process side region of the swash plate is farther from the receiving surface of the thrust bearing than the suction process side region of the swash plate when viewed from the portion corresponding to the top dead center position. The variable capacity compressor of claim 1, wherein the degree is maximized.   When the tilt angle is minimized, the compression process side region of the swash plate is farther from the receiving surface of the thrust bearing than the suction process side region of the swash plate when viewed from the portion corresponding to the top dead center position. The variable capacity compressor according to claim 1 or 2, wherein the degree is minimum and the minimum value of the tilt angle is set to approximately 0 °.

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