JP2013144957A - Variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further save energy, and to enable the lubrication of the inside when a discharge amount of a refrigerant is changed using a mechanical control valve device.SOLUTION: A variable displacement compressor 1 includes: an intake chamber communication path 62 for bringing an intake chamber Ps into communication with a crank chamber Pc; a discharge chamber communication path 63 for bringing a discharge chamber Pd2 into communication with the crank chamber Pc; a mechanical control valve device 30 for detecting refrigerant pressure inhaled to the intake chamber Ps and varying openings of the respective intake chamber communication path 62 and the discharge chamber communication path 63 to change pressure in the crank chamber Pc; and a solenoid device 31 for shutting off communication between the discharge chamber Pd2 and the intake chamber Ps in a pressure state that a piston 23 strokes, and bringing the discharge chamber Pd2 into communication with the intake chamber Ps in a pressure state that a stroke amount of the piston 23 is a minimum amount.

Description

  The present invention relates to a variable capacity compressor used in, for example, a vehicle air conditioner.

  Conventionally, a compressor constituting a refrigeration cycle of a vehicle air conditioner is driven by a vehicle engine. That is, a belt is wound around a drive pulley fixed to the crankshaft of the engine and a driven pulley of the compressor, and the power of the engine is constantly transmitted to the driven pulley by the belt. In Patent Document 1, an electromagnetic clutch mechanism is provided between the driven pulley and the drive shaft of the compressor, and the electromagnetic clutch mechanism is operated intermittently to operate the compressor only when necessary.

  Also, for example, as disclosed in Patent Document 2, a so-called variable capacity compressor configured to continuously change the discharge amount by changing the stroke amount of the piston inside the compressor is also known. ing.

  As a method of performing capacity control (discharge amount control) of the variable capacity compressor, there are an internal variable type and an external variable type. The internal variable type is a method in which the pressure on the suction side of the refrigerant, which changes according to the heat load in the passenger compartment, is detected by a mechanical control valve device, and the stroke amount of the piston is changed by this mechanical control valve device. The external variable type is, for example, a method for controlling an electric control valve device based on an external signal so as to achieve an appropriate discharge amount as disclosed in Patent Document 3.

JP 2010-112442 A JP 2009-293479 A JP 2011-80472 A

  By the way, if an electromagnetic clutch mechanism is provided as in Patent Document 1, only two states of ON and OFF of the compressor can be selected, so that it is difficult to efficiently operate with reduced surplus capacity, and the electromagnetic clutch mechanism is excited. This is disadvantageous in terms of energy saving because it consumes a lot of power.

  Further, when the compressor is repeatedly turned on and off, the surface temperature of the evaporator is likely to change, which causes a change in the temperature of the conditioned air supplied to the passenger compartment. Further, there is a concern that an impulse may occur due to torque fluctuation during the intermittent operation of the electromagnetic clutch mechanism. Furthermore, the electromagnetic clutch mechanism is heavy and causes an increase in the weight of the compressor.

  Therefore, as in Patent Document 3, it is conceivable to use an external variable type variable displacement compressor having no electromagnetic clutch mechanism. However, in the case of the external variable type, it is necessary to develop control software for controlling the electric control valve device, which increases the number of development steps. Therefore, the cost increases when viewed as a whole vehicle.

  The present invention has been made in view of the above points, and the object of the present invention is to compress the refrigerant while further saving energy when changing the discharge amount of the refrigerant using the mechanical control valve device. The purpose is to allow lubrication inside the machine.

  In order to achieve the above object, in the present invention, the circulation of the lubricating oil inside the compressor is made possible by communicating the discharge chamber and the suction chamber.

In the first invention, a suction chamber for sucking refrigerant, a compression chamber for sucking and compressing refrigerant from the suction chamber, a discharge chamber for discharging the refrigerant compressed in the compression chamber, and a crank chamber are partitioned. A casing,
A piston housed in the compression chamber;
A drive shaft disposed in the casing and driven to rotate by an external drive source;
A piston drive mechanism that converts rotational motion of the drive shaft into reciprocating motion and transmits the reciprocating motion to the piston,
In the variable capacity compressor, the piston drive mechanism is disposed in the crank chamber and is configured to change a stroke amount of the piston in accordance with a difference between a pressure in the crank chamber and a pressure in the compression chamber.
A suction chamber communication passage for communicating the suction chamber and the crank chamber;
A discharge chamber communication passage for communicating the discharge chamber and the crank chamber;
A mechanical control valve that senses the refrigerant pressure sucked into the suction chamber and changes the pressure difference between the crank chamber and the compression chamber by changing the opening of the suction chamber communication passage and the discharge chamber communication passage, respectively. Equipment,
When the pressure state of the crank chamber and the compression chamber is a pressure state that minimizes the stroke amount of the piston, the discharge chamber and the suction chamber are communicated with each other, while the pressure state of the crank chamber and the compression chamber is A communication device is provided that shuts off the communication between the discharge chamber and the suction chamber when the piston is in a pressure state in which the stroke amount is larger than the minimum stroke amount. is there.

  According to this configuration, since it is possible to change the stroke amount of the piston by the mechanical control valve device that senses the refrigerant pressure in the suction chamber, the electromagnetic clutch mechanism becomes unnecessary and the conventional electric control valve device Development of control software such as is unnecessary.

  When the stroke amount of the piston is minimum, that is, when the pressure difference between the high pressure side and the low pressure side of the refrigerant is sufficiently small, the communication chamber connects the discharge chamber and the suction chamber, so that the lubricating oil is sucked from the discharge chamber. It becomes possible to circulate in the chamber and lubricate the piston and the piston drive mechanism.

According to a second invention, in the first invention,
The communication device includes a solenoid drive device, and the position of the mechanical control valve device is changed to a normal control position for changing the pressure of the crank chamber according to the pressure of the crank chamber and the compression chamber, and the suction chamber communication. It is configured to switch to a minimum stroke position at which the passage communicates with the discharge chamber communication passage.

  According to this configuration, the mechanical control valve device itself that opens and closes the suction chamber communication passage and the discharge chamber communication passage is displaced, so that the suction chamber communication passage and the discharge chamber communication passage are communicated with each other. Communication between the chamber and the suction chamber is possible.

According to a third invention, in the second invention,
The communication device includes a solenoid drive device, and the position of the mechanical control valve device is changed to a normal control position for changing the pressure of the crank chamber according to the pressure of the crank chamber and the compression chamber, and the suction chamber communication. It is configured to switch to a minimum stroke position at which the passage communicates with the discharge chamber communication passage.

  According to this configuration, the position of the mechanical control valve device can be reliably switched between the normal control position and the minimum stroke position.

4th invention is 2nd or 3rd invention,
In the communication device, the mechanical control valve device is changed to a first normal control position for closing the discharge chamber communication passage and a second normal control position for opening the suction chamber communication passage and the discharge chamber communication passage. It is characterized by being configured.

  According to this configuration, the mechanical control valve device can be displaced to two normal control positions using the communication device. Thereby, for example, it is possible to perform control to reduce the stroke amount of the piston so that the temperature state of the evaporator is slightly higher than that in general cooling.

According to a fifth invention, in the first invention,
The casing is formed with a communication hole for communicating the suction chamber and the discharge chamber,
The communication device includes a valve that opens and closes the communication hole, and a valve body drive device that drives the valve to switch the communication hole between a closed state and an open state.

  According to this configuration, it is possible to connect the discharge chamber and the suction chamber at an arbitrary timing by opening and closing the communication hole with the valve.

  According to the first aspect of the present invention, the variable displacement compressor using the mechanical control valve device can reduce the cost by reducing the development man-hours, and the discharge is performed when the piston stroke amount is minimum. Since the piston and the piston drive mechanism can be lubricated by communicating the chamber and the suction chamber, further energy saving can be achieved. Further, since the electromagnetic clutch mechanism can be omitted, the weight can be reduced, and the temperature change of the conditioned air can be suppressed, and the urgency at the time of operation does not occur, so that passenger comfort can be improved.

  According to the second invention, since the mechanical control valve device is displaced to open and close the suction chamber communication passage and the discharge chamber communication passage, a compressor having a communication structure between the suction chamber and the discharge chamber is provided. It can be configured simply.

  According to the third aspect of the invention, the position of the mechanical control valve device can be reliably switched between the normal control position and the minimum stroke position using the solenoid drive device, and the lubrication is ensured when the stroke amount of the piston is minimum. Can be done.

  According to the fourth invention, since the mechanical control valve device can be displaced to two normal control positions using the communication device, for example, the temperature state of the evaporator is slightly higher than the normal state. By doing so, it is also possible to perform economic operation while suppressing the energy consumption of the external drive source.

  According to 5th invention, the communicating hole of a casing can be opened and closed at arbitrary timings.

It is sectional drawing of a variable capacity compressor when heat load is high. FIG. 2 is a view corresponding to FIG. 1 when the heat load is low. FIG. 2 is a view corresponding to FIG. 1 when the stroke of the piston is minimum. FIG. 3 is a view corresponding to FIG. 1 according to the second embodiment. FIG. 4 is a diagram corresponding to FIG. 3 according to the second embodiment. FIG. 10 is a diagram corresponding to FIG. 1 when in the eco mode according to the second embodiment. FIG. 10 is a view corresponding to FIG. 1 according to the third embodiment. FIG. 6 is a view corresponding to FIG. 3 according to the third embodiment. FIG. 10 is a view corresponding to FIG. 1 according to a fourth embodiment. FIG. 6 is a diagram corresponding to FIG. 3 according to a fourth embodiment. FIG. 10 is a diagram corresponding to FIG. 1 when in the eco mode according to the fourth embodiment. FIG. 10 is a view corresponding to FIG. 1 according to the fifth embodiment. FIG. 9 is a view corresponding to FIG. 3 according to the fifth embodiment. FIG. 10 is a view corresponding to FIG. 1 when in the eco mode according to the fifth embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

(Embodiment 1)
FIG. 1 shows a variable capacity compressor 1 according to a first embodiment of the present invention. This variable capacity compressor 1 constitutes one element of the refrigeration cycle of the vehicle air conditioner, and is disposed between the evaporator and the condenser.

  The variable capacity compressor 1 includes a control device 10 and a compressor body 20. The compressor body 20 includes a casing 21, a drive shaft 22, a plurality of pistons 23, 23, a piston drive mechanism 26 that converts the rotational motion of the drive shaft 22 into a reciprocating motion and transmits the reciprocating motion to the pistons 23, 23, a machine A type control valve device 30 and a solenoid drive device (communication device) 31 are provided.

  The casing 21 is formed in a substantially cylindrical shape. The drive shaft 22 has a posture extending in the center line direction of the casing 21 and is accommodated in the casing 21. Although not shown, the drive shaft 22 is rotatably supported with respect to the casing 21 by a bearing member. One end of the drive shaft 22 penetrates through the end wall portion on the one side in the center line direction of the casing 21 (left side in FIG. 1) and protrudes to the outside. A pulley 35 is fixed to one end of the drive shaft 22. There is no electromagnetic clutch mechanism between the pulley 35 and the drive shaft 22, and both are directly connected. Although not shown, the rotational force of an engine-side pulley fixed to a crankshaft of an engine (external drive source) is transmitted to the pulley 35 via a belt. Accordingly, the drive shaft 22 always rotates during the operation of the engine.

  A suction chamber Ps, a discharge chamber Pd, compression chambers Pa and Pa, and a crank chamber Pc are defined in the casing 21. The suction chamber Ps and the discharge chamber Pd are located on the other end side in the center line direction (the right side in FIG. 1) inside the casing 21, and are arranged in the circumferential direction of the center line. The compression chamber Pa is located adjacent to one side in the center line direction of the suction chamber Ps and the discharge chamber Pd. A partition 40 is provided between the compression chamber Pa and the suction chamber Ps and the discharge chamber Pd. Is provided. A plurality of compression chambers Pa are provided around the drive shaft 22 and are partitioned so as not to communicate with each other. The crank chamber Pc is positioned so as to be adjacent to one side in the center line direction of the compression chamber Pa.

  The piston 23 is accommodated in each compression chamber Pa. Each piston 23 can reciprocate in the direction of the center line of the drive shaft 22 while sliding on the inner surface of the compression chamber Pa. A recess 23 a that engages with the piston drive mechanism 26 is formed at the base end of the piston 23.

  As the piston drive mechanism 26, for example, a mechanism disclosed in Japanese Patent Application Laid-Open No. 2009-293479 can be used. In this embodiment, the piston drive mechanism 26 is housed in the crank chamber Pc, is fixed to the drive shaft 22 and rotates integrally with the drive shaft 22, and a swash plate through which the drive shaft 22 passes. 45, a boss 46 fixed to the swash plate 45, and a coil spring 47 that urges the swash plate 45.

  The rotor 44 is formed in a disk shape. A protruding plate 44 a is fixed to the side surface of the rotor 44. An arm 46 a extending from the boss 46 is connected to the protruding plate 44 a through a pin 48 so as to be swingable. The pin 48 is inserted into a groove 44b (shown in FIG. 3) formed in the protruding plate 44a. The groove 44b extends along the track drawn by the pin 48 when the inclination angle of the swash plate 45 with respect to the drive shaft 22 is changed. Therefore, the inclination of the swash plate 45 is allowed by the formation of the groove 44b. become. The rotational force of the drive shaft 22 is transmitted to the swash plate 45 through the rotor 44 and the boss 46.

  The coil spring 47 is arranged coaxially with the drive shaft 22 on one side in the center line direction of the drive shaft 22 with respect to the boss 46. One end of the coil spring 47 is in contact with the side surface of the rotor 44, and the other end is in contact with the side surface of the boss 46. The biasing force of the coil spring 47 biases the swash plate 45 toward the other side in the center line direction of the drive shaft 22 so that the swash plate 45 is in a posture (shown in FIG. 3) orthogonal to the center line of the drive shaft 22. Acts as follows. A state in which the swash plate 45 and the center line of the drive shaft 22 are nearly orthogonal is a state in which the inclination angle of the swash plate 45 is close to zero, which is the minimum stroke amount.

  A pair of shoes 50, 50 whose outer surfaces are arcuate surfaces are fixed to the outer peripheral portions of both side surfaces of the swash plate 45. The shoes 50 are inserted into the recesses 23a of the pistons 23 so as to be in sliding contact with the inner surfaces of the recesses 23a. When the swash plate 45 rotates with respect to the drive shaft 22 (shown in FIGS. 1 and 2), each piston 23 reciprocates, and the stroke amount of each piston 23 changes due to the change in the inclination angle of the swash plate 45. It is supposed to be.

  When the pressure in the crank chamber Pc is made lower than the pressure in the compression chamber Pa and the differential pressure exceeds a predetermined value, the swash plate 45 (shown in FIG. 3) having the smallest inclination angle resists the biasing force of the coil spring 47. Then, it is inclined with respect to the drive shaft 22 (shown in FIGS. 1 and 2). By changing the differential pressure between the crank chamber Pc and the compression chamber Pa, the inclination angle of the swash plate 45 can be changed steplessly. As will be described later, this differential pressure is generated by the refrigerant pressure in the suction chamber Ps.

  In the partition portion 40 of the casing 21, a suction hole 40 a is formed at a portion corresponding to the suction chamber Ps so as to communicate the suction chamber Ps and the compression chamber Pa. A suction-side check valve 51 is provided on the compression chamber Pa side of the partition 40. The suction side check valve 51 is for preventing the refrigerant sucked into the compression chamber Pa from the suction chamber 40a from flowing back into the suction chamber Ps.

  Further, the partition portion 40 of the casing 21 is formed with a discharge hole 40b at a portion corresponding to the discharge chamber Pd so that the discharge chamber Pd and the compression chamber Pa communicate with each other. A discharge-side check valve 52 is provided on the discharge chamber Pd side of the partition unit 40. The discharge side check valve 52 is for preventing the refrigerant discharged from the compression chamber Pa to the discharge chamber Pd from flowing back into the compression chamber Pa.

  In each figure, only one suction hole 40a, discharge hole 40b, suction-side check valve 51, and discharge-side check valve 52 are shown. However, the suction hole 40a and the discharge hole correspond to each compression chamber Pa. 40b, a suction-side check valve 51 and a discharge-side check valve 52 are provided.

  Further, a downstream check valve 54 is provided in the discharge chamber Pd of the casing 21. By the downstream check valve 54, the discharge chamber Pd is partitioned into a first discharge chamber Pd1 on the downstream side and a second discharge chamber Pd2 on the upstream side. The downstream check valve 54 is for preventing the refrigerant from being sucked in from the discharge side of the compressor 1, and is a closing member that opens and closes the passage 55 between the first discharge chamber Pd1 and the second discharge chamber Pd2. 54 a and a spring 54 b that urges the closing member 54 a in the closing direction of the passage 55.

  The biasing force by the spring 54b is set so as to close the passage 55 by the closing member 54a when the stroke amount of the piston 23 is minimum and to open when the stroke amount is larger than the minimum stroke amount.

  Further, a cylindrical portion 58 is provided in the vicinity of the center portion on the surface of the partition portion 40 on the crank chamber Pc side. The other end of the drive shaft 22 is rotatably supported while being inserted into the inner hole of the cylindrical portion 58. A plurality of compression chambers Pa can be partitioned by the cylindrical portion 58.

  The casing 21 is provided with a first partition wall 60 and a second partition wall 61 for partitioning the suction chamber Ps and the discharge chamber Pd. The first partition wall 60 is disposed on the suction chamber Ps side, and the second partition wall 61 is disposed on the discharge chamber Pd side.

  A through hole 40 c is formed at the center of the partition 40. The through hole 40 c communicates with the space R between the first partition wall 60 and the second partition wall 61 and the inner hole of the cylindrical portion 58.

  The cylindrical portion 58 is formed with a communication hole 21a for communicating the space R with the crank chamber Pc.

  A suction chamber communication passage 62 for communicating the suction chamber Ps and the crank chamber Pc is formed in the first partition wall 60 so as to penetrate the first partition wall 60. The suction chamber communication passage 62 communicates with the crank chamber Pc through the space R between the first partition wall 60 and the second partition wall 61 and the communication hole 22 a of the drive shaft 22.

  The second partition wall 61 is formed with a discharge chamber communication passage 63 through which the second discharge chamber Pd2 and the crank chamber Pc communicate with each other. The discharge chamber communication path 63 and the suction chamber communication path 62 are disposed so as to overlap each other when viewed along the penetration direction of the partition walls 60 and 61. Further, the discharge chamber communication passage 63 communicates with the crank chamber Pc through the space R between the first partition wall 60 and the second partition wall 61 and the communication hole 22a of the drive shaft 22.

  The mechanical control valve device 30 is disposed in the suction chamber Ps. The mechanical control valve device 30 senses the refrigerant pressure sucked into the suction chamber Ps, and changes the pressure in the crank chamber Pc by changing the opening degrees of the suction chamber communication passage 62 and the discharge chamber communication passage 63, respectively. It is operated by the refrigerant pressure regardless of the control software.

  That is, the mechanical control valve device 30 includes a base portion 30a supported on the inner wall of the casing 21, a bellows 30b fixed to the base portion 30a, and a valve rod 30c fixed to the end portion of the bellows 30b opposite to the base portion 30a. And a suction side valve body 30d and a discharge side valve body 30e formed on the valve rod 30c.

  The bellows 30b expands when the pressure in the suction chamber Ps is lower than the pressure in the bellows 30b and extends upward as shown in FIG. 2, while the pressure in the suction chamber Ps and the pressure in the bellows 30b are increased. When equilibrium is reached, the original shape is restored. On the contrary, if the pressure in the suction chamber Ps is higher than the pressure in the bellows 30b, the pressure shrinks downward.

  The valve rod 30c extends straight from the suction chamber Ps through the suction chamber communication passage 62 and the discharge chamber communication passage 63 until it reaches the first discharge chamber Pd1.

  The discharge side valve body 30e is positioned in the second discharge chamber Pd2 at the tip end of the valve rod 30c. The discharge side valve element 30e closes the discharge chamber communication path 63 by coming into contact with the opening peripheral edge of the discharge chamber communication path 63 on the second discharge chamber Pd2 side from the second discharge chamber Pd2 side, and moves away from the opening peripheral edge. As a result, the discharge chamber communication path 63 is opened. The opening degree of the discharge chamber communication path 63 is changed depending on the distance between the discharge side valve body 30e and the opening periphery of the discharge chamber communication path 63.

  The suction side valve body 30d is positioned in the suction chamber Ps closer to the base end than the discharge side valve body 30e of the valve rod 30c. The suction side valve body 30d closes the suction chamber communication passage 62 by contacting from the suction chamber Ps side with respect to the opening peripheral edge of the suction chamber communication passage 62 on the suction chamber Ps side, and away from the peripheral edge of the suction chamber. The communication path 62 is opened. The opening degree of the suction chamber communication path 62 is changed depending on the distance between the suction side valve body 30d and the opening periphery of the suction chamber communication path 62.

  The relative positional relationship between the suction side valve body 30d and the discharge side valve body 30e is such that the discharge side valve body 30e closes the discharge chamber communication path 63 when the suction side valve body 30d shown in FIG. In addition, when the suction side valve body 30d shown in FIG. 2 closes the suction chamber communication path 62, the discharge side valve body 30e opens the discharge chamber communication path 63.

  The movement timing of the suction side valve body 30d and the discharge side valve body 30e can be set by the configuration of the bellows 30b. In this embodiment, the following setting is made. When strong cooling is performed as in summer and the heat load in the passenger compartment is high, the temperature of the refrigerant immediately after passing through the evaporator is high, and the pressure of the refrigerant is also high. In this case, the pressure of the refrigerant in the suction chamber Ps increases. When such a heat load is high, the bellows 30b contracts greatly. As a result, the suction side valve body 30d and the discharge side valve body 30e move downward, the suction chamber communication path 62 is opened, and the discharge chamber communication path 63 is closed.

  On the other hand, when the heat load in the passenger compartment is low, such as during weak cooling, the temperature of the refrigerant immediately after passing through the evaporator is low, and the pressure of the refrigerant is also low. In this case, the pressure of the refrigerant in the suction chamber Ps becomes lower than that during the strong cooling described above. When such a heat load is low, the bellows 30b expands. As a result, the suction side valve body 30d and the discharge side valve body 30e move upward, the suction chamber communication path 62 is closed, and the discharge chamber communication path 63 is opened.

  When between the strong cooling and the weak cooling, the pressure of the refrigerant in the suction chamber Ps is an intermediate pressure between the strong cooling and the weak cooling. In this case, the degree of expansion of the bellows 30b is lower than that during weak cooling, and both the suction chamber communication passage 62 and the discharge chamber communication passage 63 are partially opened.

  The solenoid driving device 31 includes an electromagnetic coil 31a fixed to the inner surface of the suction chamber Ps of the casing 21, and a magnetic body 31b fixed to the base 30a of the mechanical control valve device 30. The mechanical control valve device It is for switching the position of 30. The electromagnetic coil 31 a is controlled by the control device 10. The magnetic body 30b is located in a recess formed in the casing 21 as shown in FIG. 1 when no voltage is applied to the electromagnetic coil 31a. The position of the mechanical control valve device 30 at this time is a normal control position where the discharge amount is changed when the stroke amount of the piston 23 is other than the minimum stroke amount.

  When a voltage is applied to the electromagnetic coil 31a, a force in a direction protruding into the suction chamber Ps acts on the magnetic body 31b, thereby moving the mechanical control valve device 30 upward as shown in FIG. The position of the mechanical control valve device 30 at this time is the position when the stroke amount of the piston 23 is the minimum, and is the minimum stroke position. When the stroke amount is minimum, the minimum stroke position is set so that both the suction chamber communication passage 62 and the discharge chamber communication passage 63 are opened, as shown in FIG.

  Whether or not to apply a voltage to the electromagnetic coil 31a is determined by the control device 10 detecting a thermal load. For example, assuming that there is no thermal load when the air conditioner is in the OFF state, a voltage is applied to the electromagnetic coil 31a to bring the mechanical control valve device 30 to the minimum stroke position. On the other hand, the room temperature setting by the occupant is much larger than the vehicle interior temperature. If the temperature is too low, it is determined that the thermal load is high, and the mechanical control valve device 30 is set to the normal control position without applying a voltage to the electromagnetic coil 31a. Thus, the control apparatus 10 according to the present embodiment can be very simple control software.

  Next, the operation of the variable capacity compressor 1 configured as described above will be described.

  When the heat load of the passenger compartment is high, the position of the mechanical control valve device 30 is the normal control position as shown in FIG. Further, since the pressure of the refrigerant in the suction chamber Ps is higher than the pressure in the bellows 30b, the bellows 30b of the mechanical control valve device 30 is greatly contracted, the suction chamber communication passage 62 is opened, and the discharge chamber communication passage 63 is closed. Is done. As a result, the refrigerant flows from the crank chamber Pc through the communication hole 21a and flows into the suction chamber Ps through the through hole 40c, the space R, and the suction chamber communication passage 62, so that the swash plate 45 is greatly inclined. When the drive shaft 22 rotates in this state, the swash plate 45 rotates with a large inclination, so the stroke amount of each piston 23 increases. Accordingly, a large amount of refrigerant is sucked into the compression chamber Pa from the suction chamber Ps through the suction hole 40a and compressed, and then flows out to the second discharge chamber Pd2 through the discharge hole 40b. The refrigerant that has flowed out into the second discharge chamber Pd2 passes through the passage 55, and is opened to the outside through the first discharge chamber Pd1 by opening the downstream check valve 54 by the pressure. When the heat load is high, the discharge amount increases as the stroke amount of the piston 23 increases.

  When the heat load of the vehicle compartment becomes lower than that described above, the pressure of the refrigerant in the suction chamber Ps becomes low, so that the bellows 30b of the mechanical control valve device 30 expands, the suction chamber communication passage 62 is closed, and the discharge chamber The communication path 63 is opened. At this time, the pressure of the refrigerant in the crank chamber Pc is higher than when the heat load is high, so the inclination angle of the swash plate 45 is reduced. Thereby, since the stroke amount of the piston 23 becomes small, the discharge amount decreases. The pressure of the refrigerant in the suction chamber Ps differs according to the heat load, and the inclination angle of the swash plate 45 changes accordingly, and the discharge amount changes.

  For example, when the air conditioner is turned off and there is no thermal load on the passenger compartment, as shown in FIG. 3, the control device 10 applies a voltage to the electromagnetic coil 30 a of the solenoid device 31 to change the mechanical control valve device 30. Set to the minimum stroke position. At the minimum stroke position, the mechanical control valve device 30 opens both the suction chamber communication path 62 and the discharge chamber communication path 63. As a result, the suction chamber Ps and the second discharge chamber Pd2 communicate with each other, so that the lubricating oil can flow and the circulation is promoted, so that the piston 23 and the piston drive mechanism 26 that are always operating can be lubricated. It becomes possible.

  As described above, in the variable capacity compressor 1 according to the first embodiment, the stroke amount of the piston 23 can be changed by the mechanical control valve device 30 that senses the refrigerant pressure in the suction chamber Ps. In addition, the electromagnetic clutch mechanism is unnecessary, and development of control software such as a conventional electric control valve device is not required.

  By eliminating the need for an electromagnetic clutch mechanism, it is possible to reduce the weight of the variable capacity compressor 1, further suppress the temperature change of the air-conditioning air, and improve the comfort of passengers because there is no impulse during operation. it can.

  By using the mechanical control valve device 30, the cost can be reduced by reducing the development man-hours, and the piston 23 and the piston drive mechanism 26 are lubricated when the stroke amount of the piston 23 is minimum. Therefore, further energy saving can be achieved.

(Embodiment 2)
FIGS. 4-6 shows the variable capacity compressor 1 concerning Embodiment 2 of this invention. The variable capacity compressor 1 of the second embodiment is different from that of the first embodiment in that the position of the mechanical control valve device 30 can be switched in three ways, and the other parts are the same as those of the first embodiment. Therefore, the parts different from the first embodiment will be described in detail below.

  The solenoid device 70 according to the second embodiment includes a first electromagnetic coil 70a, a first magnetic body 70b, a second electromagnetic coil 70c, and a second magnetic body 70d. The first electromagnetic coil 70 a is fixed to the deep side of the recess of the casing 21, and the second electromagnetic coil 70 c is fixed to the shallow side of the recess of the casing 21. The first magnetic body 70b is fixed to the end of the base 30a, and the second magnetic body 70d is fixed to the side of the base 30a close to the bellows 30b. Thus, two sets of electromagnetic coils and magnetic bodies are provided.

  The control apparatus 10 can apply a voltage separately to the first electromagnetic coil 70a and the second electromagnetic coil 70c.

  The first magnetic body 70b and the second magnetic body 70d are located in the recess of the casing 21 when no voltage is applied to the first electromagnetic coil 70a and the second electromagnetic coil 70c. The position of the mechanical control valve device 30 at this time is a first normal control position where the discharge amount can be changed when the stroke amount of the piston 23 is other than the minimum stroke amount, as shown in FIG. is there.

  In addition, when a voltage is applied to the first electromagnetic coil 70a and no voltage is applied to the second electromagnetic coil 70c, the second magnetic body 70d protrudes into the suction chamber Ps as shown in FIG. The magnetic body 70b is located in the recess. As a result, the entire mechanical control valve device 30 moves upward, so that the suction side valve body 30 d approaches the peripheral edge of the opening of the suction chamber communication path 62. Accordingly, the inclination angle of the swash plate 45 is reduced and the stroke amount of the piston 23 is reduced. The discharge amount can be changed even in this position, which is the second normal control position. Thus, by reducing the stroke amount of the piston 23, the cooling capacity is reduced but the energy consumption can be reduced. For example, when the eco-mode is provided in the air conditioner, the mechanical control valve device 30 is changed to the first mode. Control may be performed so that the normal control position is 2.

  The eco mode is a mode in which weak cooling is performed, and the air temperature in the vicinity of the downstream side of the air flow of the evaporator is 3 ° C. in the normal mode (cooling capacity priority mode), for example, 10 ° C. In this mode,

  When a voltage is applied to the first electromagnetic coil 70a and the second electromagnetic coil 70c, the mechanical control valve device 30 reaches the minimum stroke position, and both the suction chamber communication path 62 and the discharge chamber communication path 63 are opened. Thereby, the piston 23 and the piston drive mechanism 26 can be lubricated.

  As described above, the variable capacity compressor 1 according to the second embodiment can reduce the cost by reducing the development man-hours by using the mechanical control valve device 30 as in the first embodiment. In addition, since the piston 23 and the piston drive mechanism 26 can be lubricated when the stroke amount of the piston 23 is the minimum, further energy saving can be achieved.

  In addition, for example, a cool storage material is provided on the evaporator itself or on the downstream side of the air flow of the evaporator, and the capacity storage mode is set in the capacity priority mode when the vehicle is running, and the vehicle is stopped by waiting for a signal, for example. Sometimes, idling stop time can be ensured for a long time while suppressing idling of the engine and using the regenerator material as a cold heat source to prevent the passenger from feeling uncomfortable.

  Further, by using the eco mode, even when the vehicle hardly stops, it is possible to reduce the load on the engine and achieve fuel saving.

(Embodiment 3)
7 and 8 show a variable capacity compressor 1 according to Embodiment 3 of the present invention. The variable capacity compressor 1 of Embodiment 3 is provided with a communication hole 73 for communicating the point where the mechanical control valve device 30 is fixed and the suction chamber Ps and the second discharge chamber Pd2, and opens and closes the communication hole 73. Since it is different from that of the first embodiment in the point of doing so and other parts are the same as those of the first embodiment, the parts different from the first embodiment will be described in detail below.

  That is, in the third embodiment, the base portion 30 a of the mechanical control valve device 30 is directly fixed to the inner surface of the casing 21.

  In addition, an external passage S communicating with the space R between the first partition wall 60 and the second partition wall 61 is provided on the end wall portion on the other side in the center line direction of the casing 21. In addition, a communication hole 73 communicating with the external passage S is provided in the end wall portion so as to penetrate the end wall portion. Further, a valve 74 for opening and closing the communication hole 73 and a solenoid device 75 for driving the valve 74 are provided on the end wall portion.

  The valve 74 includes a valve rod 74 a extending in the direction of penetration of the communication hole 73 and a valve body 74 b fixed to the end of the valve rod 74 a, and is movable in the direction of penetration of the communication hole 73. The valve body 74b is disposed on the second discharge chamber Pa2 side.

  The solenoid device 75 includes an electromagnetic coil 75a fixed to the end wall portion of the casing 21 and a magnetic body 75b fixed to the other end portion of the valve rod 74a. The electromagnetic coil 75 a is controlled by the control device 10. When a voltage is applied to the electromagnetic coil 75a, the magnetic body 75b is located in a recess formed in the casing 21 as shown in FIG. 7, and at this time, the communication hole 73 is closed by the valve body 74b. On the other hand, when no voltage is applied to the electromagnetic coil 75a, the valve body 74b is separated from the communication hole 73 toward the second discharge chamber Pd2 as shown in FIG. 8, and the communication hole 73 is opened. The control device 10 is configured to apply a voltage to the electromagnetic coil 75a when the stroke of the piston 23 is other than the minimum, and not to apply it when the stroke is the minimum.

  As a result, when the stroke of the piston 23 is minimum, the suction chamber Ps and the second discharge chamber Pd2 can be communicated with each other, so that the lubricating oil can be moved back and forth, and circulation is promoted. The mechanism 26 can be lubricated.

  As described above, the variable capacity compressor 1 according to the third embodiment can reduce the cost by reducing the development man-hour by using the mechanical control valve device 30 as in the first embodiment. In addition, since the piston 23 and the piston drive mechanism 26 can be lubricated when the stroke amount of the piston 23 is the minimum, further energy saving can be achieved.

(Embodiment 4)
FIGS. 9-11 shows the variable capacity compressor 1 concerning Embodiment 3 of this invention. The variable capacity compressor 1 according to the fourth embodiment adds the configuration of the third embodiment to the configuration of the first embodiment, and can cope with a so-called eco mode.

  When the stroke of the piston 23 is other than the minimum and in the eco mode, as shown in FIG. 11, the mechanical control valve device 30 is moved upward by the solenoid drive device 31, and the suction side valve body 30d is moved to the suction chamber communication passage 62. To approach. Accordingly, the inclination angle of the swash plate 45 is reduced and the stroke amount of the piston 23 is reduced. Since the discharge amount can be changed even in this position, the mechanical control valve device 30 is in the normal control position. Thus, by reducing the stroke amount of the piston 23, the cooling capacity is reduced, but the energy consumption can be reduced. At this time, the valve 74 is kept closed.

  When the stroke is other than the minimum and the eco mode is not set, the mechanical control valve device 30 is positioned below as shown in FIG. As a result, the suction chamber communication passage 62 is opened, and the stroke amount of the piston 23 can be increased. At this time, the valve 74 is kept closed.

  Further, as shown in FIG. 10, when the stroke of the piston 23 is the minimum, the valve 74 is opened and the suction chamber Ps and the second discharge chamber Pd2 are communicated with each other as in the third embodiment.

  As described above, the variable capacity compressor 1 according to the fourth embodiment can reduce the cost by reducing the development man-hours by using the mechanical control valve device 30 as in the first embodiment. In addition, since the piston 23 and the piston drive mechanism 26 can be lubricated when the stroke amount of the piston 23 is the minimum, further energy saving can be achieved.

(Embodiment 5)
12-14 shows the variable capacity compressor 1 concerning Embodiment 3 of this invention. The variable capacity compressor 1 of the fourth embodiment is different from that of the first embodiment in that the mechanical control valve device 30 is fixed and the eco mode can be realized, and other parts are the same as those in the first embodiment. Therefore, the parts different from the first embodiment will be described in detail below.

  In the fifth embodiment, similarly to the third embodiment, the outer wall S, the communication hole 73, the first valve 74 for opening and closing the communication hole 73 and the first valve 74 for driving the valve 74 are provided on the end wall portion of the casing 21. 1 solenoid device 75 is provided. Further, a branch passage T branched from the external passage S is provided in the end wall portion, and a communication hole 80 communicating with the branch passage T is provided so as to penetrate the end wall portion. Furthermore, a second valve 81 for opening and closing the communication hole 80 and a second solenoid device 82 for driving the first valve 74 are provided on the end wall portion. The second valve 81 is configured similarly to the first valve 74, and includes a valve rod 81a and a valve body 81b. The second solenoid device 82 includes an electromagnetic coil 82a and a magnetic body 82b.

  Further, the casing 21 is provided with a valve 85 configured to suppress a rapid flow of the refrigerant from the external passage S to the branch passage T.

  In the fifth embodiment, when the stroke of the piston 23 is other than the minimum and in the eco mode, the first valve 74 is closed and the second valve 81 is opened as shown in FIG.

  When the stroke of the piston 23 is other than the minimum and the eco mode is not set, the first valve 74 and the second valve 81 are closed as shown in FIG.

  When the stroke of the piston 23 is minimum, as shown in FIG. 13, the first valve 74 and the second valve 81 are opened, and the suction chamber Ps and the second discharge chamber Pd2 are communicated.

  As described above, the variable capacity compressor 1 according to the fifth embodiment can reduce the cost by reducing the development man-hours by using the mechanical control valve device 30 as in the first embodiment. In addition, since the piston 23 and the piston drive mechanism 26 can be lubricated when the stroke amount of the piston 23 is the minimum, further energy saving can be achieved.

  As described above, the variable capacity compressor according to the present invention can be applied to, for example, a vehicle air conditioner.

DESCRIPTION OF SYMBOLS 1 Variable capacity compressor 21 Casing 22 Drive shaft 23 Piston 26 Piston drive mechanism 30 Mechanical control valve apparatus 31 Solenoid apparatus (communication apparatus)
62 Suction chamber communication passage 63 Discharge chamber communication passage 73 Communication hole 74 Valve 75 Solenoid device (valve drive device)
Ps Suction chamber Pa Compression chamber Pd1 First discharge chamber Pd2 Second discharge chamber Pc Crank chamber

Claims (5)

A casing in which a suction chamber for sucking refrigerant, a compression chamber for sucking and compressing the refrigerant from the suction chamber, a discharge chamber for discharging the refrigerant compressed in the compression chamber, and a crank chamber are defined;
A piston housed in the compression chamber;
A drive shaft disposed in the casing and driven to rotate by an external drive source;
A piston drive mechanism that converts rotational motion of the drive shaft into reciprocating motion and transmits the reciprocating motion to the piston,
In the variable capacity compressor, the piston drive mechanism is disposed in the crank chamber and is configured to change a stroke amount of the piston in accordance with a difference between a pressure in the crank chamber and a pressure in the compression chamber.
A suction chamber communication passage for communicating the suction chamber and the crank chamber;
A discharge chamber communication passage for communicating the discharge chamber and the crank chamber;
A mechanical control valve that senses the refrigerant pressure sucked into the suction chamber and changes the pressure difference between the crank chamber and the compression chamber by changing the opening of the suction chamber communication passage and the discharge chamber communication passage, respectively. Equipment,
When the pressure state of the crank chamber and the compression chamber is a pressure state that minimizes the stroke amount of the piston, the discharge chamber and the suction chamber are communicated with each other, while the pressure state of the crank chamber and the compression chamber is A variable capacity, characterized in that a communication device is provided that blocks communication between the discharge chamber and the suction chamber when the piston is in a pressure state where the stroke amount is larger than when the stroke amount is minimum. Compressor. The variable capacity compressor according to claim 1.
When the pressure state of the crank chamber and the compression chamber is a pressure state that minimizes the stroke amount of the piston, the communication device displaces the mechanical control valve device to displace the suction chamber communication passage and the compression chamber. A variable capacity compressor configured to communicate with a discharge chamber communication path. The variable capacity compressor according to claim 2,
The communication device includes a solenoid drive device, and the position of the mechanical control valve device is changed to a normal control position for changing the pressure of the crank chamber according to the pressure of the crank chamber and the compression chamber, and the suction chamber communication. A variable capacity compressor configured to switch to a minimum stroke position at which a passage and the discharge chamber communication passage communicate with each other. The variable capacity compressor according to claim 2 or 3,
In the communication device, the mechanical control valve device is changed to a first normal control position for closing the discharge chamber communication passage and a second normal control position for opening the suction chamber communication passage and the discharge chamber communication passage. A variable capacity compressor characterized by being configured to do so. The variable capacity compressor according to claim 1.
The casing is formed with a communication hole for communicating the suction chamber and the discharge chamber,
The communication device includes a valve that opens and closes the communication hole, and a valve body drive device that drives the valve to switch the communication hole between a closed state and an open state. .

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