JP2011012548A - Variable displacement swash plate type compressor and air conditioner system using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement swash plate type compressor wherein it is possible to prevent decreases in performance caused by restricting a suction path in an operating area in which low pressure pulsation does not occur, and to sufficiently reduce low pressure pulsation by restricting a suction path in an operating area that is prone to the occurrence of low pressure pulsation, and an air conditioner system using the compressor.SOLUTION: This variable displacement swash plate type compressor 4 is provided with: a suction throttle valve 62 that is disposed in a suction path 61 for guiding a coolant that has been sucked from a suction inlet 60 to a suction chamber 54 and that adjusts the path area for the coolant that passes through the suction path 61; and a solenoid valve 70 that arbitrarily adjusts the aperture of the suction throttle valve 62. The solenoid valve 70 may be one that adjusts the aperture of the suction throttle valve 62 by regulating the pressure in a back pressure chamber 68 of the suction throttle valve 62 or one that directly controls the aperture of the suction throttle valve 62 depending on the applied electric energy.

Description

  The present invention relates to a piston type compressor having a mechanism for preventing pressure pulsation caused by self-excited vibration of a suction valve from propagating outside the compressor and generating abnormal noise, and more specifically, pressure pulsation occurs. A variable capacity swash plate compressor that restricts the suction passage in the operation region to reduce the propagation of pressure pulsation outside the compressor, and avoids the suction passage being restricted in the operation region where the pressure pulsation does not occur, resulting in performance degradation. The present invention relates to an air conditioning system using this.

Conventionally, in a piston compressor, a stopper having a predetermined depth is formed at a position facing the tip of the suction valve of the cylinder block, and when the refrigerant gas is sucked into the cylinder bore, the tip of the suction valve is By contacting the stopper, the suction valve is prevented from causing self-excited vibration.
However, in a piston type variable capacity compressor, the amount of gas sucked into the cylinder bore is different between the maximum capacity and the variable capacity. Therefore, if the stopper depth is set according to the maximum capacity, the suction is especially small. Since the amount of displacement of the valve is small, the tip of the suction valve does not hit the stopper. For this reason, the suction valve causes self-excited vibration, which causes a problem that the pressure fluctuation of the gas in the suction chamber is generated, and this pressure pulsation propagates outside the compressor to generate noise.

For this reason, conventionally, the countermeasures shown in Patent Document 1 and Patent Document 2 described below have been taken.
Among these, the configuration shown in Patent Document 1 is provided with an opening control valve for controlling the opening area in the suction passage of the compressor, and this opening control valve is provided with a differential pressure and a spring force due to the gas flow in the suction passage. By operating it, the suction passage is throttled when the suction flow rate is small, and the suction pulsation generated at the small capacity is prevented from propagating outside the compressor, and the opening area of the suction passage is increased when the suction flow rate is large. I am doing so.

  In the configuration shown in Patent Document 2, an opening degree control valve for adjusting the opening degree of the suction passage is provided on the suction passage based on the differential pressure between the suction pressure and the crank chamber pressure. Using the crank chamber pressure that changes accordingly, it is easy to maximize the opening by weakening the influence of the spring force at the maximum capacity, and to reduce the opening degree by increasing the influence of the spring force at the small capacity. is doing.

JP 2001-136776 JP 2005-337232 A

  However, in the configuration of Patent Document 1 described above, since the opening degree control valve is operated using the differential pressure due to the gas flow in the suction passage and the spring force, if the spring force is set strongly with emphasis on pulsation reduction, When the capacity is reduced, the suction passage is throttled and the cooling capacity is lowered. Conversely, if the spring force is set weakly with emphasis on the cooling capacity at the maximum capacity, the pulsation cannot be sufficiently reduced at the low capacity where the throttling effect is required. There is an inconvenience.

  In general, the variable capacity compressor has a structure in which the inclination angle of the swash plate is changed based on the difference between the pressure in the cylinder bore acting on each piston and the crank chamber pressure. The pressure in the cylinder bore is substantially equal to the pressure in the suction chamber when the piston is at the bottom dead center, and gradually increases as the refrigerant gas is compressed by the piston. When the pressure in the cylinder bore exceeds the pressure in the discharge chamber, the valve is opened due to the pressure difference before and after the discharge valve, and refrigerant gas is discharged into the discharge chamber. That is, the pressure in the cylinder bore changes from the suction pressure to the discharge pressure (strictly, a little higher due to delay in opening of the discharge valve and resistance) during one rotation of the swash plate, and the pressure always acts on the piston. .

  Since the pressure in the cylinder bore acting on the piston acts in the direction of increasing the inclination angle of the swash plate, even if the pressure difference between the suction chamber and the crank chamber is the same, the higher the discharge pressure, the relatively the inclination angle The swash plate is controlled at an angle with a large (discharge capacity is large).

  For this reason, the opening adjustment valve disclosed in Patent Document 2 adjusts the opening based on the differential pressure between the suction chamber pressure and the crank chamber pressure regardless of the discharge pressure. If the opening adjustment valve is set to throttle the suction passage when the difference between the pressure in the suction chamber and the suction chamber exceeds 0.1 MPa, the swash plate is used when the pressure in the discharge chamber is low (for example, 0.8 MPa) The opening control valve does not operate until the inclination angle of the swash plate is 30% or less, and when the pressure in the discharge chamber is high (for example, 2.5 MPa), the opening adjustment valve is operated with the inclination angle of the swash plate being 70% or less Can begin to throttle the suction passage. This means that low pressure pulsation does not occur and it is not necessary to restrict the intake passage, and that the intake passage is restricted at the time of high load and the performance is impaired. It was impossible to achieve both cooling capacity and pulsation reduction corresponding to the load conditions.

  The present invention has been made in view of such circumstances, and in the operation region where the low pressure pulsation does not occur, the suction passage is restricted so that the performance is not deteriorated, and in the operation region where the low pressure pulsation is likely to occur. The main object is to provide a variable capacity swash plate compressor capable of sufficiently reducing the low pressure pulsation by narrowing the suction passage and an air conditioner system using the same.

  In order to achieve the above-mentioned problems, the present inventors have solved the above-mentioned inconvenience if the refrigerant passage area of the suction passage that guides the refrigerant sucked into the compressor to the suction chamber can be arbitrarily adjusted from the outside. The present invention has been completed based on the knowledge that it is possible.

  That is, a variable capacity swash plate compressor according to the present invention includes a housing, a piston that reciprocates in a cylinder bore formed in the housing, a crank chamber, a suction chamber, and a discharge chamber formed in the housing, A shaft that penetrates the crank chamber and is rotatably supported by the housing, a swash plate that is housed in the crank chamber and rotates by the rotation of the shaft to reciprocate the piston, and is formed in the housing. A suction port for sucking a working fluid and a discharge port for discharging the working fluid; after the working fluid sucked from the suction port is guided to the suction chamber through a suction passage formed in the housing and compressed by the piston; In the configuration for discharging from the discharge port through the discharge chamber, the passage area of the refrigerant passing through the suction passage is adjusted in the suction passage. The inlet throttle valve is provided, it is characterized in that a external adjustment means for adjusting arbitrarily based the opening degree of the intake throttle valve to an external request (command).

  According to such a configuration, the suction throttle valve is provided in the suction passage of the compressor, and further, the external adjustment means for arbitrarily adjusting the opening degree of the suction throttle valve based on a request from the outside is provided. During medium to high capacity operation under high discharge pressure conditions, even if the crank chamber pressure rises by a predetermined amount, the opening of the intake throttle valve can be kept fully open by an external adjustment means, and low pressure pulsation occurs Under such conditions, the suction throttle valve can be steadily suppressed by operating the suction throttle valve by the external adjustment means.

Here, the external adjustment means may use a solenoid valve that adjusts the pressure of the back pressure chamber of the suction throttle valve to adjust the opening of the suction throttle valve.
Since the opening of the suction throttle valve is adjusted by adjusting the pressure in the back pressure chamber of the suction throttle valve, even if the displacement of the solenoid valve is small, the pressure in the back pressure chamber is sufficient. The suction throttle valve can be operated.

The external adjustment means may directly control the opening of the suction throttle valve based on an external request (command).
According to such a configuration, since the opening degree of the suction throttle valve can be directly controlled based on an external request, the opening degree of the suction throttle valve can be controlled with high accuracy.

  The air conditioner system according to the present invention comprises a pipe coupling the above-described variable capacity swash plate compressor together with at least a condenser, an expansion device, and an evaporator to form a refrigeration cycle, and the suction to the variable capacity swash plate compressor A pressure control valve for controlling the pressure in the crank chamber based on the pressure in the chamber is further provided, and suction throttle control means for driving the external adjustment means in response to a request on the vehicle side is further provided.

  Here, the external adjusting means may be a solenoid valve that adjusts the pressure of the back pressure chamber of the suction throttle valve to adjust the opening of the suction throttle valve, or the suction throttle valve according to the electric energy that is input. The opening degree may be directly controlled.

According to such a configuration, since the pressure control valve controls the crank chamber pressure based on the pressure in the suction chamber, that is, the pressure downstream of the suction throttle valve, the compressor has a capacity based on the pressure downstream of the suction throttle valve. Is controlled. Here, when the external adjustment means is driven by the request from the suction throttle control means and the suction throttle valve throttles the suction passage, the pressure of the suction chamber decreases due to the throttle effect, and the pressure control valve decreases the suction pressure. As a result, the crank chamber pressure is increased, and as a result, the discharge capacity is reduced and the pressure in the suction chamber is balanced with the pressure before the suction passage is throttled.
In this way, the variable capacity compressor uses the function of self-controlling the capacity so that the pressure in the suction chamber becomes constant, and the capacity is arbitrarily reduced by giving a pressure difference at the suction throttle valve part, and at the same time a low capacity It becomes possible to suppress the propagation of low-pressure pulsation at the time.

  As described above, according to the present invention, the suction throttle valve for adjusting the passage area of the refrigerant passing through the suction passage is provided in the suction passage for guiding the working fluid sucked from the suction port to the suction chamber. Since the opening of the valve is arbitrarily adjusted based on the request from the outside by providing an external adjustment means, in the operation region where the low pressure pulsation does not occur, the suction passage is throttled and the performance is not deteriorated. Further, in an operation region where low pressure pulsation is likely to occur, low pressure pulsation can be sufficiently reduced by operating the suction throttle valve by the external adjustment means to throttle the suction passage.

FIG. 1 is a diagram showing a configuration example of an air conditioner system according to the present invention. FIG. 2 is a cross-sectional view showing a configuration example of a variable capacity swash plate compressor according to the present invention. FIG. 3 is a cross-sectional view showing the vicinity of the piston of the valve plate of the variable capacity swash plate compressor. FIG. 4 is a cross-sectional view showing a configuration example of the suction throttle valve and the external adjustment means of the variable capacity swash plate compressor according to the present invention. FIG. 5 is a flowchart showing an example of the control operation of the variable aperture mechanism. FIG. 6 is a cross-sectional view showing another configuration example of the suction throttle valve and the external adjustment means of the variable capacity swash plate compressor according to the present invention. FIG. 7 is a cross-sectional view showing still another configuration example of the suction throttle valve and the external adjustment means.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  In FIG. 1, the structural example of the refrigerating cycle 1 mounted in a vehicle is shown. The refrigeration cycle 1 includes a variable capacity swash plate compressor (hereinafter referred to as a compressor) having a pressure control valve 2 for varying the discharge capacity and a variable throttle mechanism 3 for varying the passage area of the suction path for introducing the refrigerant to the suction chamber. 4. A condenser 5 that cools the refrigerant, an expansion device 6 that decompresses the refrigerant, and an evaporator 8 that evaporates and evaporates the working fluid. In the refrigeration cycle 1, the discharge side of the compressor 4 is connected to the expansion device 6 via the condenser 5, and a high-pressure line is configured by a path from the discharge side of the compressor 4 to the inflow side of the expansion device 6. . The outflow side of the expansion device 6 is connected to the evaporator 8, and the outflow side of the evaporator 8 is connected to the suction side of the compressor 4, so that the outflow side of the expansion device 6 is connected to the suction side of the compressor 4. The low pressure line is constituted by the route to reach.

  Therefore, in the refrigeration cycle 1, the refrigerant compressed by the compressor 4 enters the condenser 5 as a high-temperature and high-pressure refrigerant, is cooled here, and is sent to the expansion device 6. Then, the pressure is reduced in the expansion device 6 to become low-temperature and low-pressure wet steam, and heat is exchanged with the air passing therethrough in the evaporator 8 to form a gas, which is then returned to the compressor 4.

  Reference numeral 10 denotes a temperature sensor that is arranged in the air conditioning passage and detects the air temperature on the outlet side of the evaporator 8. A signal from this temperature sensor, a signal from another sensor 11 that detects the vehicle interior temperature, etc. A signal from the operation panel 12 for setting the air conditioner to be operated / stopped, a target temperature in the passenger compartment, and the like is input to the control device 13.

  The control device 13 inputs the above-described various signals as data, a memory unit including a read-only memory (ROM) and a random access memory (RAM), and calls a program stored in the memory unit to obtain the data. It consists of a central processing unit (CPU) that processes and calculates control signals, a control signal output circuit that outputs control signals to the variable aperture mechanism 2, and the like. Based on signals from various sensors 10.11 and the operation panel 12, The variable aperture mechanism 3 is controlled.

  In FIG. 2, the specific structural example of the compressor 4 mentioned above is shown. The compressor includes a cylinder block 21, a rear housing 23 assembled to the rear side of the cylinder block 21 via a valve plate 22, a front side of the cylinder block 21, and a crank chamber 24 together with the cylinder block 21. And a front housing 25 that defines The front housing 25, the cylinder block 21, the valve plate 22, and the rear housing 23 are fastened in the axial direction by fastening bolts 26 to constitute the housing of the compressor 4.

  A crank chamber 24 defined by the front housing 25 and the cylinder block 21 accommodates a shaft 27 having one end protruding from the front housing 25. A clutch plate 29 is fixed to a portion of the shaft 27 protruding from the front housing 25 via a relay member 28 attached in the axial direction. A drive pulley 30 that is rotatably fitted around the boss portion 25 a of the front housing 25 is provided opposite to the clutch plate 29, and the clutch plate 29 is energized by energizing an excitation electromagnetic coil 31 embedded in the drive pulley 30. The rotational power that is attracted to the drive pulley 30 and applied to the drive pulley 30 is transmitted to the shaft 27.

  Further, one end of the shaft 27 is hermetically sealed with the front housing 25 through a seal member 32 provided between the shaft 27 and is supported rotatably by a radial bearing 33. The other end side of the shaft 27 is rotatably supported by a thrust bearing 35 accommodated in an accommodation hole 34 formed substantially at the center of the cylinder block 21 and a radial bearing 36 provided on the rear side adjacent thereto. Has been.

  The cylinder block 21 is formed with the accommodation hole 34 and a plurality of cylinder bores 37 arranged at equal intervals on a circumference centered on the accommodation hole 34. Each cylinder bore 37 has a single-head piston. 40 is inserted so that reciprocation is possible.

  A thrust flange 41 that rotates integrally with the shaft 27 is fixed to the shaft 27 in the crank chamber 24. The thrust flange 41 is rotatably supported on an inner wall surface of the front housing 25 formed substantially perpendicular to the shaft 27 via a thrust bearing 42. A swash plate 44 is connected to the thrust flange 41 via a link member 43.

  The swash plate 44 is held so as to be tiltable via a hinge ball 45 provided on the shaft 27, and rotates integrally with the rotation of the thrust flange 41. The thrust flange 41 and the swash plate 44 constitute a power transmission mechanism that rotates in synchronization with the rotation of the shaft 27. And the engaging part 40a of the single-headed piston 40 is moored by the peripheral part of the swash plate 44 via a pair of shoes 46 provided in the front and back.

  Accordingly, when the shaft 27 is rotated, the swash plate 44 is rotated accordingly, and the rotational motion of the swash plate 44 is converted into the reciprocating linear motion of the one-headed piston 40 via the shoe 46, and The volume of the compression chamber 47 (shown in FIG. 3) defined by the valve plate 22 is changed.

  As shown in FIG. 3, the valve plate 22 is opened and closed by a suction hole 51 opened and closed by a suction valve 50 provided on the cylinder block side end surface and a discharge valve 52 provided on the rear housing side end surface. A discharge hole 53 is formed corresponding to each cylinder bore 37. Further, the rear housing 23 is formed with a suction chamber 54 for storing the refrigerant supplied to the compression chamber 47 and a discharge chamber 55 for storing the refrigerant discharged from the compression chamber 47. In this example, the suction chamber 54 is formed substantially at the center of the rear housing 23, and the discharge chamber 55 is formed around the suction chamber 54.

  The suction valve 50 is sandwiched between the cylinder block 21 and the valve plate 22 together with the suction valve side gasket 56, and the discharge valve 52 is sandwiched between the valve plate 22 and the rear housing 23 together with the discharge valve side gasket 57. Has been.

The intake valve side gasket 56 is disposed between the cylinder block 21 and the intake valve 50 and is provided so as to surround each cylinder bore 37. A suction valve stopper 58 that restricts the opening operation of the suction valve 50 is formed at the end of the cylinder bore 37 on the valve plate side. The suction valve stopper 58 is formed by cutting to a predetermined depth at a position facing the tip of the suction valve 50. In this example, the depth of the stopper is set in accordance with the amount of suction gas at the intermediate capacity. ing.
Further, the discharge valve side gasket 57 is disposed between the discharge valve 52 and the rear housing 23 and is provided so as to surround the suction hole 51 and regulates the valve opening operation of the discharge valve 52. A discharge valve stopper 59 is integrally formed.

  The rear housing 23 has a suction port 60 for sucking refrigerant from the external cycle, a suction passage 61 for leading the refrigerant sucked from the suction port 60 to the suction chamber 54, and a discharge port for discharging the refrigerant to the external cycle. (Not shown) and a discharge passage (not shown) for guiding the refrigerant discharged to the discharge chamber to the discharge port are formed.

  A suction throttle valve 62 is disposed on the suction passage 61 connecting the suction port 60 and the suction chamber 54 as shown in FIG. The suction throttle valve 62 is housed in a valve housing chamber 63 formed in the middle of the suction passage 61 so as to be displaceable in the refrigerant flow direction, and is biased in the valve opening direction by a spring 64 elastically mounted in the valve housing chamber 63. Has been.

  Specifically, the valve housing chamber 63 is formed to have a diameter larger than the diameter of the suction passage 61 by aligning the axial center with the suction passage 61 extending from the suction port 60, and suction is performed on the side surface of the valve housing chamber 63. The communication portion 66 that communicates with the chamber 54 is opened, and the suction throttle valve 62 is formed in a cylindrical shape with one end open and the other end closed, and the valve housing chamber 63 faces the closing portion 62a toward the suction port side. And is urged in a direction away from the suction port 60 by a spring 64 elastically mounted on the suction port side of the valve storage chamber 63. The communication portion 66 is fully opened without being blocked by the side surface of the suction throttle valve 62 when the suction throttle valve 62 is urged by the spring 64 and is located farthest from the suction port 60, and the suction throttle valve 62 is fully opened. When the valve is displaced toward the suction port side, it is throttled by the side surface of the suction throttle valve 62 so that the opening degree becomes small.

  An orifice 67 is formed in the closing portion 62 a of the suction throttle valve 62, and a back pressure chamber 68 is formed inside the suction throttle valve 62. The back pressure chamber 68 and the suction passage 61 communicate with each other via the orifice 67. ing. Therefore, the suction throttle valve 62 is displaced to a position where the pressure upstream of the suction chamber (pressure of the suction passage 61), the pressure of the back pressure chamber 68, and the spring force of the spring 64 are balanced, and the pressure of the back pressure chamber 68 is reduced. Unless increased, the pressure in the back pressure chamber 68 and the pressure in the suction passage 61 are balanced via the orifice 67, and the communication portion 66 is fully opened by the spring force of the spring 64 (the opening degree of the suction throttle valve 62 is maximum). It becomes.

  The adjustment of the opening degree of the suction throttle valve 62, that is, the pressure adjustment of the back pressure chamber 68 is performed by a solenoid valve 70 described below that constitutes an external preparation means. The suction throttle valve 62 and the solenoid valve 70 constitute the variable throttle mechanism 3.

  The solenoid valve 70 is housed in the rear housing 23, and the rod portion 75 of the valve body 73 is slidably disposed in a shaft hole 72 formed in the center of a cylindrical body 71. The valve body 73 has a head 74 that is formed to have a diameter larger than the diameter of the shaft hole 72 and is seated on the periphery of the opening of the shaft hole 72, and a rod portion 75 that extends from the head 74. In the portion 75, a constricted portion 75a having a relatively small diameter from the head 74 to a predetermined range is formed.

  A communication chamber 76 that communicates with the back pressure chamber 68 of the suction throttle valve 62 and communicates with the shaft hole 72 is provided at the distal end portion of the body 71, and the communication chamber 76 includes a head 74 of the valve element 73 and the head 74. A valve spring 77 for energizing the valve body 73 in the closing direction (downward in the figure) is accommodated.

  In addition, the body 71 communicates with the shaft hole 72, and a cylindrical cylinder 80 that is housed and fixed with the shaft hole 72 aligned with the shaft center, and an electromagnetic coil 81 wound around the cylinder 80, A plunger 82 which is slidably inserted into the cylinder 80 and abuts against the rod portion 75 of the valve body 73 which is inserted through the shaft hole 72; and an adjustment cap 83 which is attached to the proximal end opening end of the cylinder 80; And a spring 84 which is elastically mounted between the back surface of the plunger 82 and the adjustment cap 83 and urges the plunger 82 toward the valve element side (the upper side in the figure).

A discharge pressure introduction port 85 for introducing the pressure of the discharge chamber 55 is provided at the center of the side surface of the solenoid valve 70, and further, a suction for introducing the pressure of the suction chamber 54 below (on the side opposite to the back pressure chamber). A pressure introducing port 86 is provided.
The discharge pressure introduction port 85 extends in the radial direction of the body 71 and opens on the side surface of the shaft hole 72 that faces the constricted portion 75 a of the valve body 73. The suction pressure introduction port 86 extends in the radial direction of the body 71 and communicates with a groove 87 formed on the inner peripheral surface of the shaft hole 72. The suction pressure introduction port 86 receives the suction pressure introduced from the suction pressure introduction port 86. The valve body 73 is guided to the lower surface.

  Therefore, the force for attracting the plunger 82 downward can be adjusted by adjusting the energization amount to the electromagnetic coil 81. When the electromagnetic coil 81 is not energized, the plunger 82 is a spring 84 provided under the plunger. , And the valve element 73 is opened against the valve spring 77. As a result, the high-pressure gas introduced through the discharge pressure introduction port 85 passes around the constricted portion 75 a formed in the valve body 73 and reaches the communication chamber 76, and the back pressure chamber 68 is passed through the communication chamber 76. Led to.

  On the other hand, when the electromagnetic coil 81 is energized so as to generate an attractive force that overcomes the spring force, the plunger 82 moves downward and the valve element 73 moves downward due to the spring force of the valve spring 77. Displacement closes the shaft hole 72. Since the shaft hole 72 is formed straight, the area on which the high pressure introduced into the constricted portion 75a of the valve body 73 acts is the same on the upper surface and the lower surface of the constricted portion 75a, and the discharge pressure is high. However, the valve element 73 is prevented from opening due to the influence of the discharge pressure.

  In addition, since the suction pressure introduced from the suction pressure introduction port 86 wraps around the lower surface of the valve body 73, when the pressure in the back pressure chamber 68 is almost equal to the pressure in the suction chamber 54, the influence of the suction pressure. Will also be canceled. That is, the opening degree of the solenoid valve is controlled only by the energization amount to the electromagnetic coil 81 without being affected by the pressure.

  Further, since the gas introduced into the back pressure chamber 68 via the solenoid valve 70 communicates with the suction pressure region through the orifice 67 provided in the center of the suction throttle valve 62, the back pressure chamber 68 is passed through the solenoid valve 70. The pressure in the back pressure chamber 68 can be adjusted by the balance between the amount of gas introduced into the gas and the amount of gas released through the orifice 67.

  In the above-described compressor, a known pressure control valve 2 that adjusts the pressure in the crank chamber 24 based on the pressure in the suction chamber 54 is further provided in the rear housing 23. This type of pressure control valve 2 adjusts the crank chamber pressure by causing a pressure sensitive member such as a bellows or a diaphragm to correspond to the suction pressure and moving the valve body by the pressure sensitive member when the suction pressure falls below a predetermined value. It is like that. As a method of adjusting the crank chamber pressure, when the suction pressure falls below a predetermined value, the valve seat is opened and the discharge pressure is introduced into the crank chamber 24, and the amount of gas released from the crank chamber 24 to the suction chamber 54 is limited. In this embodiment, the pressure control valve 2 adjusts the communication state of the air supply passage 89 that connects the discharge chamber 55 and the crank chamber 24. A configuration is adopted in which the high-pressure gas in the discharge chamber 55 is introduced into the crank chamber 24. The pressure of the crank chamber 24 is controlled by the pressure control valve 2, and the piston stroke, that is, the discharge capacity is adjusted.

In FIG. 5, an example of the control operation of the variable aperture mechanism 3 by the control device 13 is shown as a flowchart. By this control operation, suction throttle control means for driving the solenoid valve in response to a request on the vehicle side is configured.
Hereinafter, based on this flowchart, the control operation example of the variable throttle mechanism 3 will be described. First, the control device 13 determines whether or not the compressor 4 is in a stopped state when a stop command for the air conditioner is issued (step). S01). In this determination, if it is determined that the air conditioner is in a stopped state, the control signal (Dt) to the solenoid valve 70 of the variable throttle mechanism 3 is set to zero (the current supplied to the solenoid is zero) (step) S02). As a result, the plunger 82 is pushed upward in the drawing by the spring force of the spring 84 and the valve body 73 is moved upward accordingly, and a high pressure is introduced into the back pressure chamber 68 so that the suction throttle valve resists the spring 64. The suction passage 61 is blocked by closing the communication portion 66.

  If it is determined in step S01 that the air conditioner is in operation, the evaporator outlet air temperature (Te) is higher than the evaporator outlet air set temperature (Te (set)) in step S03. In step S04, it is determined whether the air temperature (Te) at the evaporator outlet is lower than the air set temperature (Te (set)) at the evaporator outlet. When it is determined that Te) is higher than the air set temperature (Te (set)) at the outlet of the evaporator, the air temperature blown out from the evaporator 8 is higher than the set temperature. In order to move in the fully open direction, the control signal (duty ratio: Dt) is set large (the amount of current supplied to the solenoid) is set (step S05). As a result, the plunger 82 is sucked downward, the valve body 73 is displaced in the closing direction (downward in the figure) by the spring force of the valve spring 77, and the pressure supply to the back pressure chamber 68 is restricted, so that the back pressure chamber 68. The pressure difference between the suction passage 61 and the suction passage 61 is reduced, and the suction throttle valve 62 is displaced downward by the spring force of the spring 64 to reduce the throttle of the suction passage 61 (open the communicating portion 66 to reduce the throttle resistance).

On the other hand, when it is determined that the air temperature (Te) at the evaporator outlet is lower than the air set temperature (Te (set)) at the evaporator outlet, the air temperature blown from the evaporator is lower than the set temperature. Since it is low, the control signal (Dt) is set to be small (the amount of current supplied to the solenoid) is small in order to move the suction throttle valve 62 in the fully closed direction (step S06). As a result, the plunger 82 is displaced upward by the spring force of the spring 84, the valve body 73 is displaced in the opening direction against the spring force of the valve spring 77, and a large amount of high-pressure refrigerant is supplied to the back pressure chamber 68. Therefore, the pressure difference between the back pressure chamber 68 and the suction passage 61 is increased, the suction throttle valve 62 is displaced upward against the spring force of the spring 64, and the throttle of the suction passage 61 is increased.
If it is determined that the air temperature (Te) at the outlet of the evaporator is the same as the air set temperature (Te (set)) at the outlet of the evaporator, the current control amount is maintained (step S07).

Therefore, the operation state of the compressor according to the heat load in the passenger compartment based on the above control of the intake throttle valve will be described as follows.
<(1) Full capacity operation>
When the passenger compartment is not sufficiently cooled, the pressure (intake pressure) on the low pressure side of the refrigeration cycle 1 is high. In such a case, it is necessary to ensure sufficient cooling capacity, and it is not a condition for generating pulsation. Therefore, the suction throttle control means supplies a current equal to or greater than a predetermined value so that the solenoid valve 70 remains fully closed. The electromagnetic coil 81 is given. As a result, the pressure in the back pressure chamber 68 is equalized with the pressure in the suction passage 61, the suction throttle valve 62 is kept fully open by the spring force of the spring 64, and the pressure in the suction chamber 54 is sufficiently high, so that the pressure control valve 2 is also operated. Instead, the swash plate 44 is operated at the maximum inclination angle, and the compressor 4 maintains the operation at the maximum capacity.

<(2) Intermediate capacity operation>
As the passenger compartment cools, the heat load on the evaporator 8 also decreases, and the suction pressure decreases. At this time, if the outlet air temperature of the evaporator 8 is not lower than the target air temperature, the refrigerating capacity is not excessive yet, so that the suction throttle control means exceeds the predetermined value so that the solenoid valve 70 is kept in the fully closed state. Is supplied to the electromagnetic coil 81. As a result, the suction throttle valve 62 is kept fully open. When the pressure in the suction chamber 54 of the compressor 4 falls below a predetermined value, the bellows of the pressure control valve 2 expands to open the valve seat, the high-pressure gas in the discharge chamber is introduced into the crank chamber 24, and the inclination angle of the swash plate 44 Is reduced, the capacity of the compressor 4 is reduced, and a reduction (overcooling) of the suction pressure is prevented.

<(3) Low capacity operation + suction restriction>
When the outlet air temperature of the evaporator 8 falls below the target outlet air temperature due to a further decrease in the heat load or a change in the vehicle interior temperature, the refrigerating capacity is excessive. The amount of current supplied to 70 is reduced, and a high pressure is introduced into the back pressure chamber 68. The suction throttle valve 62 throttles the suction passage 61 according to the pressure difference between the increased back pressure chamber 68 and the suction passage 61, and the pressure in the suction chamber 54 decreases. Since the pressure control valve 2 increases the pressure in the crank chamber 24 to reduce the capacity of the compressor 4 based on the decrease in the pressure in the suction chamber 54, the refrigeration capacity is reduced, and as a result, the pressure in the suction chamber 54 is reduced. Kept constant. At this time, the pressure upstream of the suction throttle valve 62, that is, the pressure on the evaporator 8 side of the refrigeration cycle is higher than the pressure in the suction chamber 54 due to the pressure difference before and after the suction throttle valve 62. Capability control similar to the configuration in which the set suction pressure of the valve 2 is increased to reduce the refrigeration capability is obtained.
Although it is a region where suction pulsation occurs due to low capacity operation at low load, since the suction passage 61 is throttled by the suction throttle valve 62, propagation of pulsation to the vehicle side can be suppressed.

  In the above-described embodiment, the intake throttle valve 62 opens and closes along the flow of the intake gas. However, as shown in FIG. The movement of 62 may be orthogonal to the flow of intake gas.

  In this example, a valve body sliding passage 90 orthogonal to the suction passage 61 is provided in the rear housing 23, and a spool-like suction throttle valve 62 is slidably disposed in the valve body sliding passage 90, and A similar solenoid valve 70 is attached to face the suction throttle valve 62 in the axial direction so that the movement of the suction throttle valve 62 is controlled.

The suction throttle valve 62 is formed with a small diameter portion 62a at an intermediate portion, a first sliding portion 62b urged toward the solenoid valve 70 by a spring 91 at one end, and a refrigerant of the suction passage 61 at the other end. A second sliding portion 62c that changes the cross section of the passage through which the gas flows is formed. The portion in which the spring 91 is accommodated communicates with the suction chamber 54, and a back pressure chamber 68 is formed between the second sliding portion 62c and the tip of the solenoid valve 70, and this back pressure chamber. 68 communicates with the suction passage 61 through an orifice 67 formed in the second sliding portion 62c. Therefore, in a state where the pressure in the back pressure chamber 68 and the pressure in the suction passage 61 are balanced, the suction throttle valve 62 is urged by the spring 91, and the second sliding portion 62c is disengaged from the suction passage 61. The small diameter portion 62 a faces the suction passage 61. If the pressure in the back pressure chamber 68 is relatively higher than the pressure in the suction passage 61, the suction throttle valve 62 is displaced to the left in the figure against the spring force of the spring 91, and the second sliding portion. The suction passage 61 is gradually throttled at 62c, and the suction passage 61 is blocked when the suction passage 61 is displaced to the leftmost.
In addition, since the other structure is the same as that of the said structural example, it attaches | subjects the same code | symbol to the same location, and abbreviate | omits description. Such a configuration also has the same operational effects as the above configuration example.

  In the above-described configuration, the back pressure chamber 68 is provided on the back surface of the suction throttle valve 62, and the suction throttle valve 62 is moved using the pressure force. However, as shown in FIG. The suction throttle valve 62 may be driven.

  In this example, the suction throttle valve 62 disposed in the middle of the suction passage 61 is integrated with the solenoid valve 70 so as to function as a plunger, and the cylindrical suction throttle valve 62 closed at one end is The shaft 71 is movably accommodated in a shaft hole 72 formed in the body 71 and is slidably inserted into a cylindrical cylinder 80 which is fixed to the shaft hole 72 of the body 71 with its axis aligned. The body 71 has an inlet 92 communicating with the shaft hole 72 at the tip thereof, and an outlet 93 communicating with the shaft hole 72 on the side surface thereof, so that the suction throttle valve 62 contacts the tip of the body 71. Then, the inflow port 92 is closed.

  Further, the variable throttle mechanism 3 includes an electromagnetic coil 81 wound around the cylinder 80 and an adjustment cap 83 attached to the proximal end opening of the cylinder 80 in order to drive and control the suction throttle valve 62. A spring 84 is provided between the adjustment cap 83 and the suction throttle valve 62 and biases the suction throttle valve 62 toward the inlet 92. Note that the pressure in the suction chamber 54 is guided to the inside of the suction throttle valve 62 through the body 71, the cylinder 80, and through holes 94, 95, 96 formed in the suction throttle valve 62.

  Therefore, by controlling the energization amount to the electromagnetic coil 81, the force for attracting the suction throttle valve 62 downward can be adjusted. When the electromagnetic coil 81 is not energized, the suction throttle valve 62 is moved upward by the spring 84. The inlet 92 formed in the body 71 is closed, and the suction passage 61 is blocked.

  On the other hand, when the electromagnetic coil 81 is energized so as to generate an attractive force that overcomes the spring force of the spring 84, the suction throttle valve 62 moves downward, and the magnetic force, the pressure of the suction passage 61, the suction It stops at a position where the pressure of the chamber 54 and the spring force of the spring 84 are balanced. When the suction throttle valve 62 is displaced downward, the suction throttle valve 62 is disengaged from the outlet 93, and the communication state between the inlet 92 and the outlet 93 is maximized. In addition, the size of the inflow port 92 and the outflow port 93 has a sufficient passage area so that pressure loss does not occur even in the high refrigerant flow rate operation where the communication state is maximum.

  Therefore, even in the configuration in which the suction throttle valve 62 and the solenoid valve 70 are integrated, the opening degree of the suction throttle valve can be maintained in a fully opened state during medium to high capacity operation under a high discharge pressure condition. In addition, under conditions where low-pressure pulsation occurs, it is possible to suppress the propagation of suction pulsation.

In the first and second embodiments described above, the back pressure chamber 68 and the solenoid valve 70 are disposed adjacent to each other. However, the back pressure chamber 68 and the solenoid 70 are separated from each other and communicated with the back pressure chamber 68. The chamber 76 may be connected by a gas passage so that the pressure in the communication chamber 76 is guided to the back pressure chamber 68 through the gas passage.
In the control operation example shown in FIG. 5 described above, the variable throttle mechanism 3 is controlled with the heat load of the refrigeration cycle as a control target. However, the variable throttle mechanism 3 is controlled by detecting or estimating the occurrence of pulsation. You may do it.
Furthermore, in the above-described pressure control valve, an example of an internal control type has been shown. However, the pressure control valve is an external control valve that can change the pressure set point by an external force such as a solenoid, and is in accordance with the heat load of the refrigeration cycle. The refrigeration capacity control may be assigned to this external control valve instead of the suction throttle valve. In this case, it is possible to obtain more accurate capacity control and pulsation reduction by making the operation command of the suction throttle valve a factor of occurrence of pulsation.
Furthermore, in the first and second embodiments described above, the intake throttle valve is a valve that follows the flow of the intake gas, or a spool valve that is orthogonal to the flow of the intake gas, but the butterfly valve is rotated by a predetermined angle by the external adjustment means. The suction passage may be throttled.

DESCRIPTION OF SYMBOLS 1 Refrigerating cycle 2 Pressure control valve 3 Variable throttle mechanism 4 Compressor 5 Condenser 6 Expansion device 8 Evaporator 21 Cylinder block 22 Valve plate 23 Rear housing 25 Front housing 37 Cylinder bore 40 Piston 44 Swash plate 54 Suction chamber 55 Discharge chamber 60 Suction Port 61 Suction passage 62 Suction throttle valve 68 Back pressure chamber 70 Solenoid valve

Claims (4)

A housing, a piston that reciprocates in a cylinder bore formed in the housing, a crank chamber, a suction chamber, and a discharge chamber formed in the housing, and penetrates the crank chamber and is rotatably supported by the housing. A shaft, a swash plate that is housed in the crank chamber and is rotated by the rotation of the shaft to reciprocate the piston, and a suction port that is formed in the housing and sucks a working fluid and a discharge port that discharges the working fluid. A variable capacity that guides the working fluid sucked from the suction port to the suction chamber via a suction passage formed in the housing, and discharges the working fluid from the discharge port through the discharge chamber after being compressed by the piston In swash plate compressor,
The suction passage is provided with a suction throttle valve that adjusts the passage area of the refrigerant that passes through the suction passage, and is provided with an external adjustment means that arbitrarily adjusts the opening of the suction throttle valve based on a request from the outside. A variable capacity swash plate compressor.   2. The variable capacity swash plate compressor according to claim 1, wherein the external adjustment means is a solenoid valve that adjusts the opening of the suction throttle valve by adjusting the pressure of the back pressure chamber of the suction throttle valve. .   2. The variable capacity swash plate compressor according to claim 1, wherein the external adjustment means directly controls the opening of the suction throttle valve based on an external request. The variable capacity swash plate compressor according to any one of claims 1 to 3 is connected to a pipe together with at least a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle,
The variable capacity swash plate compressor is further provided with a pressure control valve for controlling the pressure of the crank chamber based on the pressure of the suction chamber,
An air conditioner system further comprising suction throttle control means for driving the external adjustment means in response to a request on the vehicle side.

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