JP2018159322A - Clutchless variable displacement swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutchless variable displacement swash plate compressor in which a high-pressure coolant is unlikely to be discharged to the outside even if a driving source rotationally drives a drive shaft at high speed in a case where a check valve is provided between a discharge chamber and the outside.SOLUTION: A clutchless variable displacement swash plate compressor comprises a partition body 49, a movable body 43, a control pressure chamber 51 and a control mechanism 80. A pressure in the control pressure chamber 51 is reduced, thereby reducing an inclination angle θ of a swash plate 29. A check valve 75 is provided between the first and second discharge chambers 1b and 7b and the outside. The swash plate 29, a link mechanism 40 and pistons 53 are configured in such a manner that, when the inclination angle θ becomes smaller than a predetermined angle θ1, the inclination angle θ is decreased by a total of products of inertia of the swash plate 29, the link mechanism 40 and the pistons 53.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a clutchless variable capacity swash plate compressor.

  Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter simply referred to as a compressor). The compressor includes a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a partition body, a moving body, a control pressure chamber, and a control mechanism.

  The housing is formed with a swash plate chamber, a discharge chamber, and a plurality of cylinder bores. The drive shaft is rotatably supported by the housing. The swash plate is disposed in the swash plate chamber and is rotated together with the drive shaft. The link mechanism allows a change in the inclination angle of the swash plate with respect to the direction perpendicular to the drive axis of the drive shaft. Each piston is accommodated in each cylinder bore, and reciprocates at a stroke corresponding to the inclination angle by rotation of the swash plate to form a compression chamber in each cylinder bore. Thus, each piston compresses the refrigerant sucked into the compression chamber and discharges the high-pressure refrigerant into the discharge chamber. The partition is provided so as to rotate integrally with the drive shaft in the swash plate chamber. The movable body can rotate integrally with the drive shaft in the swash plate chamber, and moves in the direction of the drive axis with respect to the partition body to change the inclination angle. The control pressure chamber is partitioned by the partition body and the moving body, and moves the moving body by the internal pressure. The control mechanism controls the pressure in the control pressure chamber.

  The cylinder bore includes a first cylinder bore provided on one side of the swash plate and a second cylinder bore provided on the other side of the swash plate. Each piston reciprocates the first cylinder bore, and the first head that partitions the first compression chamber in the first cylinder bore and the second cylinder bore reciprocates in the second cylinder bore to partition the second compression chamber. And a second head. The inclination angle becomes smaller as the pressure in the control pressure chamber decreases.

  In this compressor, when the control mechanism makes the pressure in the control pressure chamber higher than that in the swash plate chamber, the movable body moves backward against the compression reaction force of the piston. For this reason, an inclination angle becomes large and the stroke of each piston becomes large. For this reason, the compression capacity per rotation of the compressor increases. On the other hand, when the control mechanism makes the pressure in the control pressure chamber as low as the swash plate chamber, the movable body moves forward by the compression reaction force of each piston. For this reason, an inclination angle becomes small and the stroke of a piston reduces. For this reason, the compression capacity per rotation of the compressor is reduced.

  Here, in this compressor, since the top dead center position of the second head moves larger than the top dead center position of the first head of the piston, if the inclination angle of the swash plate approaches the minimum inclination angle, A slight compression work is performed only in one compression chamber, and no compression work is performed in the second compression chamber.

Japanese Patent Laid-Open No. 2015-4308

  When the compressor as described above is used in a vehicle air conditioner, for example, in a clutchless manner, that is, when the drive shaft is connected to a drive source outside the housing without a clutch, the compressor is disposed between the discharge chamber and the outside. May be provided with a check valve. The valve opening pressure of the check valve is set larger than the pressure of the first discharge chamber when the inclination angle of the swash plate is minimum, so that high-pressure refrigerant is not discharged from the first discharge chamber to the outside. Determined.

  However, in such a compressor, when the drive source rotates the drive shaft at a high speed, a large reciprocating inertia force acts on each piston. For this reason, a moment in the direction in which the inclination angle increases acts on the swash plate, the pressure in the first discharge chamber may exceed the valve opening pressure of the check valve, and high pressure refrigerant may be discharged to the outside. In this case, for example, in a vehicle air conditioner, unnecessary cooling of the passenger compartment and unnecessary power loss occur.

  The present invention has been made in view of the above-described conventional situation, and in a clutchless variable displacement swash plate compressor in which a check valve is provided between the discharge chamber and the outside, the inclination angle of the swash plate It is an issue to be solved that it is difficult to discharge a high-pressure refrigerant to the outside even when the drive source rotates the drive shaft at a high speed when the angle is equal to or less than a predetermined angle.

A clutchless capacity variable swash plate compressor of the present invention includes a housing in which a swash plate chamber, a discharge chamber and a plurality of cylinder bores are formed,
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the drive axis of the drive shaft;
Each cylinder bore accommodates, and reciprocates at a stroke corresponding to the inclination angle by rotation of the swash plate to form a compression chamber in each cylinder bore, compresses the refrigerant sucked into the compression chamber, A piston for discharging refrigerant into the discharge chamber;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the drive axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
The inclination angle is reduced by reducing the pressure of the control pressure chamber,
A check valve is provided between the discharge chamber and the outside,
The swash plate, the link mechanism, and the pistons are configured such that when the inclination angle becomes smaller than a predetermined angle, the sum of inertial products of the swash plate, the link mechanism, and the pistons decreases the inclination angle. It is characterized by being.

  In the clutchless capacity variable swash plate compressor of the present invention, when the inclination angle of the swash plate, the link mechanism and each piston is smaller than a predetermined angle, the sum of the inertial products of the swash plate, the link mechanism and each piston is negative. become. For this reason, even when the drive source rotates the drive shaft at a high speed and a large reciprocating inertia force acts on each piston in a state where the tilt angle is smaller than a predetermined angle, a moment in the direction in which the tilt angle increases is difficult to act. The swash plate can easily maintain an inclination angle smaller than a predetermined angle. For this reason, it is suppressed that the pressure of a discharge chamber exceeds the valve opening pressure of a non-return valve.

  Therefore, in the clutchless capacity variable swash plate compressor of the present invention, when the inclination angle of the swash plate is equal to or smaller than a predetermined angle, even if the drive source rotates the drive shaft at a high speed, the high-pressure refrigerant is externally provided. Is difficult to discharge.

  Each cylinder bore may be composed of a first cylinder bore provided on one side of the swash plate and a second cylinder bore provided on the other side of the swash plate. Each piston may have a first head that partitions the first compression chamber in the first cylinder bore and a second head that partitions the second compression chamber in the second cylinder bore. In this case, since each piston is a double-headed system, a compression reaction force acts from both sides, the weight is relatively large, and a reciprocating inertial force acts more greatly on the swash plate. For this reason, in this case, the effect of the present invention becomes remarkable.

  It is preferable that the swash plate has a bulging portion that positions the center of gravity of the swash plate on the moving body side. In this case, a moment in a direction in which the inclination angle decreases due to the bulging portion acts on the swash plate, and the effect of the present invention becomes remarkable.

  It is preferable that a stopper for restricting the swash plate is provided between the drive shaft or the housing and the swash plate at a minimum inclination angle greater than 0 °. This is because if the minimum inclination angle of the swash plate becomes 0 ° or minus, it becomes difficult to recover by increasing the inclination angle.

  The stopper is preferably a spring that biases the swash plate so that the inclination angle becomes large. In this case, the swash plate can be restored from the minimum inclination angle with a simple configuration.

  In the clutchless capacity variable swash plate compressor of the present invention, when the inclination angle of the swash plate is equal to or smaller than a predetermined angle, even if the drive source rotates the drive shaft at a high speed, high pressure refrigerant is discharged to the outside. It is hard to do. For this reason, if this clutchless type variable capacity swash plate compressor is employed in, for example, a vehicle air conditioner, unnecessary cooling of the passenger compartment and unnecessary power loss are unlikely to occur, and high reliability can be exhibited. it can.

FIG. 1 is a cross-sectional view showing a state where the inclination angle is maximum in the clutchless variable capacity swash plate compressor of the embodiment. FIG. 2 is a cross-sectional view showing a state in which the inclination angle is minimum, according to the clutchless variable displacement swash plate compressor of the embodiment. FIG. 3 is a schematic diagram of a control mechanism according to the clutchless capacity variable swash plate compressor of the embodiment. FIG. 4 is a graph showing the relationship between the inclination angle and the product of inertia in the clutchless capacity variable swash plate compressor of the example. FIG. 5 is a graph showing the relationship between the rotational speed of the drive shaft and the inclination angle, etc., according to the clutchless capacity variable swash plate compressor of the embodiment. FIG. 6 is a graph showing the relationship between the rotational speed of the drive shaft and the inclination angle, etc., for a clutchless capacity variable swash plate compressor of a comparative example.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. In the clutchless capacity variable swash plate compressor (hereinafter simply referred to as a compressor) of the embodiment, as shown in FIGS. 1 and 2, the front housing 1, the first cylinder block 3, the second cylinder block 5, and The rear housing 7 is joined. Hereinafter, the front housing 1 side is defined as the front side of the compressor, and the rear housing 7 side is defined as the rear side of the compressor.

  The front housing 1 is formed with a first suction chamber 1a located on the inner peripheral side and an annular first discharge chamber 1b located on the outer peripheral side. A swash plate chamber 9 is formed between the first cylinder block 3 and the second cylinder block 5. The second cylinder block 5 is formed with a suction port 50 that opens the swash plate chamber 9 to the outside. The suction port 50 is connected to the evaporator of the refrigeration circuit.

  A plurality of first cylinder bores 3 a communicating with the swash plate chamber 9 are formed in the first cylinder block 3. The second cylinder block 5 is also formed with a plurality of second cylinder bores 5 a communicating with the swash plate chamber 9. The first cylinder bore 3a and the second cylinder bore 5a have the same number, the same diameter, and the same axis. The rear housing 7 has a pressure adjusting chamber 7c located in the center portion, and is formed in an annular shape, a second suction chamber 7a located on the outer peripheral side of the pressure adjusting chamber 7c, and is formed in an annular shape. A second discharge chamber 7b located on the outer peripheral side is formed. The front housing 1, the first cylinder block 3, the second cylinder block 5 and the rear housing 7 correspond to the housing 8.

  The front housing 1 is formed with a boss portion 1c protruding forward, and a shaft hole 1d is formed inside. A shaft seal device 11 for sealing between the first suction chamber 1a and the outside of the compressor is provided in the shaft hole 1d. The first cylinder block 3 is formed with a first recess 3b coaxial with the shaft hole 1d. A first radial bearing 13 and a first thrust bearing 15 are provided in the small diameter portion of the first recess 3b. The first radial bearing 13 is a slide bearing, and the first thrust bearing 15 is a rolling bearing.

  The second cylinder block 5 is formed with a second recess 5b coaxial with the shaft hole 1d and the first recess 3b. A second radial bearing 17 and a second thrust bearing 19 are provided in the small diameter portion of the second recess 5b. The second radial bearing 17 is a slide bearing, and the second thrust bearing 19 is a rolling bearing.

  In the shaft hole 1d, the first recess 3b, the swash plate chamber 9 and the second recess 5b, a shaft seal device 11, a first radial bearing 13, a first thrust bearing 15, a second thrust bearing 19 and a second radial bearing 17 are provided. The drive shaft 21 is rotatably supported.

  The drive shaft 21 includes a drive shaft main body 23, a first flange member 25 provided integrally with the front portion of the drive shaft main body 23, and a second flange member 27 provided integrally with the rear portion of the drive shaft main body 23. Have. The first flange member 25 has a first flange 25 a projecting radially outward, and the first flange 25 a is pivotally supported by the first thrust bearing 15. The second flange member 27 also has a second flange 27 a that protrudes radially outward, and the second flange 27 a is pivotally supported by the second thrust bearing 19.

  A swash plate 29 is disposed in the swash plate chamber 9. The swash plate 29 includes a substrate 31 having a through hole 31 a through which the drive shaft 21 is inserted, and an annular swash plate main body 33 fixed to the outer peripheral surface of the substrate 31. The substrate 31 has a bulging portion 31a that bulges rearward. The swash plate body 33 has an annular shape, and its front and rear surfaces are flat.

  A lug arm 37 is swingably provided on the first flange member 25 by a first pin 35. The first pin 35 extends in a direction orthogonal to the drive axis O of the drive shaft 21. The lug arm 37 has an insertion hole 37a through which the drive shaft 21 is inserted. The lug arm 37 is provided with a second pin 39 at a position straddling the drive shaft 21 from the first pin 35. The second pin 39 extends in parallel with the first pin 35. A substrate 31 of a swash plate 29 is swingably provided on the second pin 39. The lug arm 37 has a weight portion 37 b behind the second pin 39. A third pin 41 is provided on the bulging portion 31 a of the substrate 31. The third pin 41 extends in parallel with the first and second pins 35 and 39. A movable body 43 is swingably provided on the third pin 41. Thus, the swash plate 29 can swing around the first to third pins 35, 39, 41 orthogonal to the drive axis O to change the tilt angle θ. The first to third pins 35, 39, 41 and the lug arm 37 correspond to the link mechanism 40.

  A disc-shaped partition body 49 is fixed to the rear portion of the drive shaft main body 23 of the drive shaft 21. The drive shaft main body 23 is provided with a bottomed cylindrical moving body 43 so as to be movable in the direction of the drive axis O. A control pressure chamber 51 is partitioned by the partition body 49 and the moving body 43. The rear end position of the moving body 43 is restricted by the second flange 27a.

  The drive shaft body 23 is formed with a control passage 23a extending forward from the rear end. The control passage 23 a opens at the rear end of the drive shaft main body 23 and communicates with the pressure adjusting chamber 7 c, and opens at the peripheral surface of the drive shaft main body 23 and communicates with the control pressure chamber 51.

  A stopper spring 45 is provided between the first flange 25 a of the first flange member 25 of the drive shaft 21 and the swash plate 29. An inclination angle reduction spring 47 is provided between the partition body 49 and the swash plate 29.

  Pistons 53 are accommodated in the first cylinder bores 3a and the second cylinder bores 5a. Each piston 53 has a first head 53a that partitions the first compression chamber 55 in the first cylinder bore 3a, and a second head 53b that partitions the second compression chamber 57 in the second cylinder bore 5a. Between the swash plate main body 33 of the swash plate 29 and each piston 53, a pair of shoes 54 are provided in front and rear.

  A first valve unit 59 is sandwiched between the front housing 1 and the first cylinder block 3. A second valve unit 61 is sandwiched between the second cylinder block 5 and the rear housing 7. The first valve unit 59 includes a first suction valve mechanism 59a that opens and closes each first compression chamber 55 and the first suction chamber 1a, and a first that opens and closes each first compression chamber 55 and the first discharge chamber 1b. A discharge valve mechanism 59b is formed. The second valve unit 61 includes a second suction valve mechanism 61a for opening and closing each second compression chamber 57 and the second suction chamber 7a, and a second for opening and closing each second compression chamber 55 and the second discharge chamber 7b. A discharge valve mechanism 61b is formed.

  The first cylinder block 3 and the first valve unit 59 are formed with a plurality of first suction passages 63 communicating the swash plate chamber 9 and the first suction chamber 1a. The second cylinder block 5 and the second valve unit 61 are formed with a plurality of second suction passages 65 that communicate the swash plate chamber 9 and the second suction chamber 7a.

  The first discharge chamber 1b and the second discharge chamber 7b communicate with the front housing 1, the first valve unit 59, the first cylinder block 3, the second cylinder block 5, the second valve unit 61, and the rear housing 7. A discharge passage 69 is formed. In the second cylinder block 5, a common path 73 that connects the discharge passage 69 to the discharge port 71 is formed. A check valve 75 is provided in the common path 73. The check valve 75 opens the common path 73 with a predetermined set pressure. The discharge port 71 is connected to the condenser of the refrigeration circuit.

  As shown in FIG. 3, the control mechanism 80 has an extraction passage 81, an air supply passage 83, a capacity control valve 77, a fixed throttle 83a, and a control passage 23a.

  The extraction passage 81 is connected to the pressure adjustment chamber 7c and the second suction chamber 7a. The control pressure chamber 51, the pressure adjustment chamber 7c, and the second suction chamber 7a communicate with each other through the extraction passage 81 and the control passage 23a. The air supply passage 83 is connected to the pressure adjustment chamber 7c and the second discharge chamber 7b. The control pressure chamber 51, the pressure adjustment chamber 7c, and the second discharge chamber 7b communicate with each other by the supply passage 83 and the control passage 23a. The supply passage 83 is provided with a fixed throttle 83a.

  A capacity control valve 77 is accommodated in the rear housing 7. The capacity control valve 77 is provided in the extraction passage 81. The capacity control valve 77 can adjust the opening degree of the extraction passage 81 based on the suction pressure Ps in the second suction chamber 7a and the like.

4 shows a first axis indicating an inclination angle θ, which is an angle formed by the swash plate 29 with respect to a plane orthogonal to the drive axis O, and a second axis orthogonal to the first axis and indicating an inertial product. A rectangular coordinate system is shown. As shown in FIG. 4, in this compressor, the inertial product of the swash plate 29 is −ΔP (kgmm ² ) at an inclination angle θ = 0 °, and decreases as the inclination angle θ increases. Further, in the link mechanism 40, the inertial product of the second to third pins 39 and 41 and the lug arm 37 is substantially 0 at the inclination angle θ = 0 °, and the inclination angle θ until the inclination angle θ exceeds 15 °. Increases as the inclination angle θ increases, and the inclination angle θ increases as the inclination angle θ increases in the vicinity of the maximum inclination angle. On the other hand, the inertial product of each piston 53 and each shoe 54 is 0 at the inclination angle θ = 0 °, and increases as the inclination angle θ increases. For this reason, the sum of the inertial products of the swash plate 29, the link mechanism 40, and each piston 53 is negative when the inclination angle θ is smaller than the predetermined angle θ1.

  This compressor is used in a vehicle air conditioner in a clutchless manner. That is, as shown in FIGS. 1 and 2, the drive shaft 21 is connected to the vehicle engine without an electromagnetic clutch. When the drive shaft 21 is driven to rotate, the link mechanism 40 and the swash plate 29 rotate in the swash plate chamber 9, and the pistons 53 reciprocate in the first and second cylinder bores 3a and 5a via the shoes 54. For this reason, the first compression chamber 55 sucks and compresses the refrigerant in the first suction chamber 1a and discharges it to the first discharge chamber 1b. The second compression chamber 57 sucks and compresses the refrigerant in the second suction chamber 7a and discharges it to the second discharge chamber 7b. The refrigerant in the swash plate chamber 9 sequentially supplied from the evaporator moves to the first and second suction chambers 1a and 7a through the first and second suction passages 63 and 65. The high-pressure refrigerant in the first and second discharge chambers 1b and 7b reaches the common path 73 via the discharge passage 69, opens the check valve 75, and is discharged from the discharge port 71 to the condenser.

  Here, if the capacity control valve 77 reduces the opening degree of the extraction passage 81, the high-pressure refrigerant in the second discharge chamber 7b is supplied to the control pressure chamber 51 through the supply passage 83 and the pressure adjustment chamber 7c. The refrigerant in the control pressure chamber 51 becomes difficult to be discharged to the second suction chamber 7a through the pressure adjustment chamber 7c and the extraction passage 81, and the control pressure chamber 51 becomes high pressure. For this reason, as shown in FIG. 1, the moving body 43 moves backward, and the swash plate 29 is pulled backward. For this reason, the control pressure chamber 51 is enlarged and the inclination angle θ is increased. For this reason, each piston 53 reciprocates with a large stroke in the first and second cylinder bores 3a and 5a. For this reason, the large-capacity high-pressure refrigerant discharged into the first and second discharge chambers 1 b and 7 b opens the check valve 75 and is discharged from the discharge port 71. In this case, the compressor has a large discharge capacity per rotation of the drive shaft 21.

  On the other hand, if the capacity control valve 77 increases the opening degree of the extraction passage 81, the high-pressure refrigerant in the second discharge chamber 7b is supplied to the control pressure chamber 51 through the supply passage 83 and the pressure adjustment chamber 7c, and is controlled. The refrigerant in the pressure chamber 51 is easily discharged to the second suction chamber 7a through the pressure adjustment chamber 7c and the extraction passage 81, and the control pressure chamber 51 becomes low pressure. Therefore, as shown in FIG. 2, the swash plate 29 is pushed forward by the compression reaction force applied to the swash plate 29, and the moving body 43 is pulled by the swash plate 29 and moves forward. For this reason, the control pressure chamber 51 is reduced and the inclination angle θ is reduced. For this reason, each piston 53 reciprocates within the first and second cylinder bores 3a and 5a with a small stroke. For this reason, the small-volume high-pressure refrigerant discharged into the first and second discharge chambers 1 b and 7 b opens the check valve 75 and is discharged from the discharge port 71. In this case, the compressor has a small discharge capacity per rotation of the drive shaft 21.

  When the inclination angle of the swash plate 29 approaches 0 °, the swash plate 29 comes into contact with the stopper spring 45 and the minimum inclination angle is restricted to 0 ° or minus. Thus, when the stroke of each piston 53 is almost eliminated, the refrigerant in the common path 73 cannot open the check valve 75 and is not discharged from the discharge port 71 even though the drive shaft 21 is rotating. .

  In the meantime, in this compressor, if the inclination angle is smaller than the predetermined angle θ1, even if the engine rotates the drive shaft 21 at a high speed and a large reciprocal inertia force acts on each piston 53, the inertial product of each piston 53 Since the (reciprocating inertia force of the piston 53) is smaller than the sum of the inertial products of the swash plate 29 and the link mechanism 40, the swash plate 29 in a state where the inclination angle θ is smaller than θ1 is in the direction in which the inclination angle θ increases. The moment does not act, and the swash plate 29 tends to maintain its inclination angle θ. That is, this compressor is configured such that the sum of the inertial products of the swash plate 29, the link mechanism 40, and each piston 53 decreases the inclination angle θ.

  In particular, in this compressor, since the base plate 31 of the swash plate 29 has a bulging portion 31a that positions the center of gravity of the swash plate 29 on the moving body 43 side, the swash plate 29 has a moment in a direction in which the tilt angle θ decreases. Easy to act.

  FIG. 5 shows the relationship between the rotational speed of the drive shaft 21 and the inclination angle θ in this compressor. The relationship shown in FIG. 5 is established only when the inclination angle θ is equal to or smaller than the predetermined angle θ1 in FIG. As shown in FIG. 5, in this compressor, the differential pressure between the first and second discharge chambers 1b and 7b and the outside is substantially constant. Therefore, the check valve 75 does not exceed the valve opening pressure set so as to open the common path 73. For this reason, the inclination angle θ can be kept small regardless of the reciprocal inertia force of each piston 53.

  On the other hand, even if the inclination angle θ is smaller than the predetermined angle θ1, in the compressor of the comparative example in which the sum of the inertial products of the swash plate, the link mechanism, and each piston is positive, as shown in FIG. If it becomes high, the differential pressure between the first and second discharge chambers and the outside will exceed the valve opening pressure of the check valve. When the sum of the inertial products of the pistons 53, the link mechanism 40, and the swash plate 29 is positive, the inclination angle θ of the swash plate 29 increases as the rotational speed increases.

  Therefore, in the compressor of the embodiment, the inclination angle θ of the swash plate 29 is used in a clutchless manner, and the check valve 75 is provided between the first and second discharge chambers 1b and 7b and the outside. When the angle is equal to or smaller than the predetermined angle θ1, it is difficult to discharge high-pressure refrigerant to the outside even if the engine rotates the drive shaft 21 at high speed. For this reason, in this compressor, it is hard to produce unnecessary cooling of the passenger compartment and unnecessary power loss, and high reliability can be exhibited.

  While the present invention has been described with reference to the embodiments, it is needless to say that the present invention is not limited to the above-described embodiments and can be appropriately modified and applied without departing from the spirit thereof.

  The present invention is applicable to a vehicle air conditioner.

9 ... Swash plate chamber 1a, 7a ... Suction chamber (1a ... 1st suction chamber, 7a ... 2nd suction chamber)
1b, 7b ... discharge chamber (1b ... first discharge chamber, 7b ... second discharge chamber)
3a, 5a ... cylinder bore (3a ... first cylinder bore, 5a ... second cylinder bore)
8 ... Housing (1 ... Front housing, 3 ... First cylinder block, 5 ... Second cylinder block, 7 ... Rear housing)
21 ... Drive shaft O ... Drive shaft center 35, 39, 41 ... Pivot (35 ... First pin, 39 ... Second pin, 41 ... Third pin)
θ ... Inclination angle 29 ... Swash plate 40 ... Link mechanism (37 ... Lug arm)
55, 57 ... compression chamber (55 ... first compression chamber, 57 ... second compression chamber)
53 ... Piston 49 ... Partition body 43 ... Moving body 51 ... Control pressure chamber 80 ... Control mechanism 75 ... Check valve 53a ... First head 53b ... Second head 31a ... Swelling portion 45 ... Stopper spring

Claims (5)

A housing in which a swash plate chamber, a discharge chamber and a plurality of cylinder bores are formed;
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the drive axis of the drive shaft;
Each cylinder bore accommodates, and reciprocates at a stroke corresponding to the inclination angle by rotation of the swash plate to form a compression chamber in each cylinder bore, compresses the refrigerant sucked into the compression chamber, A piston for discharging refrigerant into the discharge chamber;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the drive axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
The inclination angle is reduced by reducing the pressure of the control pressure chamber,
A check valve is provided between the discharge chamber and the outside,
The swash plate, the link mechanism, and the pistons are configured such that when the inclination angle becomes smaller than a predetermined angle, the sum of inertial products of the swash plate, the link mechanism, and the pistons decreases the inclination angle. A clutchless capacity variable swash plate compressor characterized in that Each cylinder bore comprises a first cylinder bore provided on one side of the swash plate and a second cylinder bore provided on the other side of the swash plate,
2. The clutchless type according to claim 1, wherein each piston has a first head that partitions a first compression chamber in the first cylinder bore, and a second head that partitions a second compression chamber in the second cylinder bore. Variable capacity swash plate compressor.   3. The clutchless capacity variable swash plate compressor according to claim 1, wherein the swash plate has a bulging portion that positions the center of gravity of the swash plate on the movable body side.   The stopper which controls the said swash plate to the minimum inclination angle in which the said inclination angle is larger than 0 degree is provided between the said drive shaft or the said housing, and the said swash plate. The clutchless capacity variable swash plate compressor as described.   The clutch-less variable displacement swash plate compressor according to claim 4, wherein the stopper is a spring that biases the swash plate so that the inclination angle becomes large.

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