JP2001032787A - Variable displacement scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor capable of speedily changing delivery capacity to a prescribed capacity corresponding to fluctuation of an engine load. SOLUTION: A spool 116 is moved by balance between elastic force Fs of a coil spring 118f and a control pressure Pc of a discharge pressure Pd reduced and adjusted. By setting the elastic force Fs to be larger than force by the maximum pressure of the control pressure Pc (suction pressure Ps), the spool 116 can be moved without having effects of a thermal load of a cycle, thereby delivery capacity can be speedily changed to be reduced corresponding to fluctuation of an engine load.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement scroll compressor, and is effective when applied to a compressor of a vehicle refrigeration cycle.

[0002]

2. Description of the Related Art As a variable displacement scroll compressor for a refrigerating cycle, for example, in the invention described in Japanese Patent Application Laid-Open No. 9-296787, the operation during the compression stroke is performed by balancing the elastic force of the coil spring and the suction pressure. A spool valve that opens and closes a bypass hole that connects the chamber with the suction side is opened and closed.

However, in the invention described in the above publication, the bypass hole is opened and closed by balancing the elastic force of the coil spring and the suction pressure, so that the bypass hole is opened and closed according to the heat load of the refrigeration cycle (pressure inside the evaporator). It will open and close.

The compressor of a vehicle refrigeration cycle operates by receiving power from a traveling engine (hereinafter, simply referred to as an engine). Therefore, when the load on the engine is large, such as when climbing a slope or accelerating, the compressor is not used. In order to improve acceleration performance and fuel consumption rate (vehicle fuel efficiency), it is desirable to reduce the load on the engine by reducing the discharge capacity of the engine.

On the other hand, in the invention described in the above-mentioned publication, the bypass hole for communicating the working chamber and the suction side during the compression stroke is opened and closed by balancing the elastic force of the coil spring and the suction pressure. Since the discharge capacity cannot be changed according to the load of the engine and the engine cannot be properly controlled, it is practically impossible to improve the acceleration performance and the fuel efficiency of the vehicle.

In response to such a demand, for example, in a variable displacement swash plate type compressor described in Japanese Patent Application Laid-Open No. 2-249717, the pressure in the swash plate chamber is controlled based on the engine load, thereby reducing the swash plate pressure. The discharge capacity is changed by changing the inclination angle of the plate.

[0007]

By controlling the pressure in the swash plate chamber in accordance with the engine load, as disclosed in Japanese Patent Application Laid-Open No. 2-249717, the inventors found that the engine load fluctuated. On the other hand, the inclination angle (discharge capacity) did not change quickly, and the fuel efficiency of the vehicle could not be sufficiently improved.

[0008] Then, when the cause that the inclination angle (discharge capacity) does not change quickly with the fluctuation of the engine load was investigated, the following points were found.

That is, in the invention described in Japanese Patent Application Laid-Open No. Hei 2-249717, the inclination angle of the swash plate is controlled by balancing the compression reaction force and the pressure in the swash plate chamber. The pressure in the swash plate chamber is controlled by adjusting the suction pressure and the discharge pressure with valve means such as an electromagnetic valve and introducing the adjusted pressure into the swash plate chamber.

Here, since both the suction pressure and the discharge pressure fluctuate due to the heat load of the refrigeration cycle, even if the valve means is controlled according to the engine load, the force actually acting on the swash plate is obtained. (Compression reaction force and pressure in the swash plate chamber) are strongly affected by the heat load of the refrigeration cycle. Therefore, even if the valve means is controlled in accordance with the engine load, the inclination angle (discharge capacity) cannot be quickly changed with respect to the change in the engine load.

Further, if the discharge capacity is controlled in two stages of the maximum capacity and the minimum capacity, although the acceleration performance can be improved, the flow rate of the discharged refrigerant decreases, and the refrigeration capacity decreases. I will.

The present invention has been made in view of the above circumstances, and provides a compressor capable of controlling a required discharge capacity according to a use situation, for example, by rapidly changing a discharge capacity in response to a change in engine load. With the goal.

[0013]

According to the present invention, in order to achieve the above object, according to the first and second aspects of the present invention, an elastic force is applied to one end of the valve body (116) in its movable direction. Pressure adjusting means for reducing the discharge pressure of the compression mechanism (Cp), and applying the reduced pressure to the other end of the valve element (116) in the movable direction. (118, 123, 129).

Thus, in the present invention, the valve element (116) is moved by balancing the elastic force and the adjustment pressure. Therefore, if the elastic force is sufficiently increased, the influence of the heat load of the cycle can be reduced. The valve body (116) can be moved without receiving.

Therefore, when the load on the engine is large, such as when accelerating or climbing a hill, the pressure adjusting means (118, 1) is designed to reduce the discharge capacity of the variable displacement scroll compressor.
23, 129), it is possible to quickly reduce and change the discharge capacity in response to a change in engine load. As a result, it is possible to prevent the discharge capacity from excessively decreasing while sufficiently improving the fuel efficiency of the vehicle.

In the present invention, at least two types of working chambers (Vc) in the working chamber (Vc) during the compression stroke are used.
c) and a plurality of bypass holes (11) for communicating with the suction side.
4), the discharge capacity can be changed to at least two states of a minimum capacity, an intermediate capacity, and a maximum capacity.

According to the second aspect of the present invention, the valve element (11)
The suction pressure of the compression mechanism (Cp) acts on one end in the movable direction 6) in addition to the elastic force, and the pressure adjusting means (118) adjusts the adjustment pressure by a predetermined pressure difference from the suction pressure. The pressure reduction can be adjusted so as to have

With this arrangement, the valve body (11) has good responsiveness to the operation of the pressure adjusting means (118) without being affected by the fluctuation of the suction pressure, that is, the heat load of the cycle.
6) can be operated.

According to a third aspect of the present invention, there is provided a variable displacement scroll compressor (100) according to the first or second aspect, wherein the variable capacity scroll type compressor (100) operates by receiving a driving force from a vehicle driving source (500).
A driving load detecting means (600) for detecting a driving load of the vehicle driving source (500); and a driving load detecting means (60).
When the driving load detected in step (0) is equal to or more than a predetermined load, the control means (actuates the pressure adjusting means (118, 123, 129) to reduce the discharge capacity of the variable displacement scroll compressor (100). 700).

Thus, while sufficiently improving the acceleration performance and the fuel efficiency of the vehicle, it is possible to improve the acceleration performance as a minimum capacity operation, and to achieve both the fuel efficiency and the air conditioning capacity as an intermediate capacity operation, for example. The discharge capacity can be selected.

According to the fourth aspect of the present invention, the valve element (11)
6) Elastic means (122) for applying elastic force to one end in the movable direction, and the discharge pressure and compression mechanism of the compression mechanism (Cp) to the other end in the movable direction of the valve element (116). (Cp) a first pressure adjusting means (123) for switching and operating the suction pressure, and the other end of the valve element (116) in the movable direction is displaceable in a direction parallel to the movable direction of the valve element (116). A stopper (120) provided to regulate the movable range of the valve element (116), and a second pressure valve that switches the discharge pressure and the suction pressure to act on the opposite side of the stopper (120) from the valve element (116). A pressure adjusting means (129).

This makes it possible to quickly reduce and change the discharge capacity in response to a change in the engine load, as in the first aspect of the present invention.

According to the fifth aspect of the present invention, the valve element (11)
6) Elastic means (122) for applying elastic force to one end in the movable direction, and the discharge pressure and compression mechanism of the compression mechanism (Cp) to the other end in the movable direction of the valve element (116). (Cp) a first pressure adjusting means (123) for switching and operating the suction pressure, and the other end of the valve element (116) in the movable direction is displaceable in a direction parallel to the movable direction of the valve element (116). A stopper (120) provided to regulate the movable range of the valve element (116), and the discharge pressure and the suction pressure are made to act on the opposite side of the stopper (120) from the valve element (116) by switching. A second pressure adjusting means (129) for guiding pressure to the first pressure adjusting means (123);
The passages (126, 127) and the second pressure adjusting means (12
The second passage (132, 133) for guiding pressure to 9) is provided substantially in parallel with the gasket (150).

As a result, the first and second passages (126, 12)
7, 132, 133) are arranged in series in the axial direction of the variable displacement scroll compressor.
07) can be prevented from becoming small.
Therefore, the pressure pulsation is sufficiently smoothed,
Similarly to the invention described in the above, while sufficiently improving the acceleration performance and the fuel efficiency of the vehicle, for example, to improve the acceleration performance as a minimum capacity operation, or to achieve a balance between fuel efficiency and air conditioning capacity as an intermediate capacity operation. It is possible to select an appropriate discharge capacity.

According to the sixth aspect of the present invention, the valve body (11
6) Elastic means (122) for applying elastic force to one end in the movable direction, and the discharge pressure and compression mechanism of the compression mechanism (Cp) to the other end in the movable direction of the valve element (116). (Cp) a first pressure adjusting means (123) for switching and operating the suction pressure, and the other end of the valve body (116) in the movable direction can be displaced in a direction parallel to the movable direction of the valve body (116). A stopper (120) for restricting a movable range of the valve (116), and a discharge pressure and a suction pressure acting on a side of the stopper (120) opposite to the valve (116). The second pressure adjusting means (12
9) and elastic means (140) for applying an elastic force for pressing the stopper (120) toward the valve body (116).

Thus, the stopper (120) can be prevented from vibrating (rattle).
In the same manner as in the fourth aspect of the present invention, while improving the acceleration performance and the fuel efficiency of the vehicle, for example, while improving the acceleration performance as the minimum capacity operation, while preventing the noise caused by the vibration of 0), In addition, it is possible to select the discharge capacity according to the usage convenience, such as achieving both fuel consumption and air conditioning capacity as the intermediate capacity operation.

According to a seventh aspect of the present invention, the variable displacement scroll compressor (100) according to any one of the fourth to sixth aspects, wherein the variable displacement scroll compressor (100) is operated by obtaining a driving force from a vehicle driving source (500). A driving load detecting means (600) for detecting a driving load of the vehicle driving source (500), and a first load when the driving load detected by the driving load detecting means (600) exceeds a predetermined load. , 2 pressure adjusting means (12
And control means (700) for operating at least one of the compressors (3, 129) to reduce the discharge capacity of the variable displacement scroll compressor (100).

Thus, the acceleration performance and the fuel efficiency of the vehicle can be sufficiently improved, and the acceleration performance can be improved as a minimum displacement operation, or the fuel consumption and the air-conditioning capacity can be compatible as an intermediate displacement operation. The discharge capacity can be selected.

Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with specific means described in the embodiments described later.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
A variable displacement scroll compressor (hereinafter, abbreviated as a compressor) according to the present invention is used as a vehicle refrigeration cycle (vehicle air conditioner).
FIG. 1 is a schematic diagram of a vehicle refrigeration cycle (hereinafter, abbreviated as a cycle).

Reference numeral 100 denotes a compressor according to the present embodiment,
Reference numeral 200 denotes a condenser (radiator) for cooling the refrigerant (fluid) discharged from the compressor 100. 300 decompresses the refrigerant flowing out of the condenser 200 and evaporator 4 described later.
Reference numeral 400 denotes an expansion valve (decompressor) whose opening is controlled so that the degree of heating on the outlet side of the expansion valve becomes a predetermined value.
This is an evaporator for evaporating the liquid-phase refrigerant decompressed at.

The compressor 100 has a V-belt 510,
The vehicle is driven by a vehicle driving engine (hereinafter abbreviated as engine) 500 via a power transmission means (not shown) for transmitting power intermittently such as a pulley 520 and an electromagnetic clutch.

Reference numeral 600 denotes a driving load sensor (driving load detecting means) for detecting the opening of the load of the engine 500 (in this embodiment, a throttle valve (not shown)). An electronic control unit (ECU) that controls a pressure adjusting unit 118 (first and second solenoid valves 118c and 118d) described below according to a program set in advance based on the detected value.

Next, the structure of the compressor 100 will be described.

FIG. 2 shows a cross section of the compressor 100.
Reference numeral 101 denotes a shaft that is rotationally driven via power transmission means (an electromagnetic clutch). Reference numeral 102 denotes a front housing that holds a rolling bearing 103 that rotatably supports the shaft 101. A fixed scroll (fixed portion) 104 having a spiral tooth portion 104a is fixed to the front housing 102. .

The space formed by the fixed scroll 104 and the front housing 102 has a tooth 1
An orbiting scroll (movable portion) 105 provided with a spiral tooth portion 105a that meshes with the rotating scroll 104a is provided. The orbiting scroll 105 is a crank ( Eccentric part)
It is rotatably attached to 101a via a bearing 101b and a bushing 101c.

Incidentally, in the present embodiment, the bushing 10
1c is slightly slidable with respect to the crank portion 101a, and slides the orbiting scroll 105 in a direction in which the contact pressure between the two tooth portions 104a and 105a increases due to the compression reaction force acting on the orbiting scroll 105. As a result, the contact pressure between the teeth 104a and 105a is increased (driven crank mechanism).

Then, the orbiting scroll 105 orbits around the shaft 101 together with the rotation of the shaft 101, so that the volume of the working chamber Vc formed by the two scrolls 104 and 105 is enlarged or reduced to suck and compress the refrigerant. Hereinafter, a mechanism that sucks and compresses the refrigerant of the scrolls 104 and 105 and the like is referred to as a compression mechanism Cp.

A suction chamber 106 communicates with a suction port (not shown) connected to the outlet side of the evaporator 400.
A discharge chamber 107 communicates with a discharge port (not shown) connected to the inlet side of the condenser 200 and smoothes the pulsation of the refrigerant discharged from the working chamber Vc. And the discharge chamber 1
07 is an end plate portion (tooth portion 104a) of the fixed scroll 104.
(A plate-like portion formed at the base of the valve) 104b and communicates with the working chamber Vc through a discharge port (not shown) formed in the discharge port 107b. A reed valve-shaped discharge valve 108 for preventing backflow from the chamber 107 to the working chamber Vc is provided.

The discharge chamber 107 is connected to the fixed scroll 10 via a gasket (not shown in this embodiment).
4 and is formed in a space surrounded by the rear housing 151 fixed to the fixed scroll 104 and the fixed scroll 104. Further, the discharge valve 108 is fixedly fastened to the end plate portion 104b by bolts 110 together with a valve stop plate (valve retainer) 109 for regulating the maximum opening of the discharge valve 108.

The end plate portion 104b is formed with a bypass port (bypass hole) 114 for communicating the working chamber Vc and the suction chamber 106 during the compression stroke. The bypass port 114 is connected to the end plate portion 104b. Of these, the working chamber Vc is provided at a portion where the volume is about 50% of the maximum volume, and at a portion where the volume is about 20% of the maximum volume. Hereinafter, of the bypass ports 114, a bypass port located at a portion that accounts for 50% of the maximum volume will be referred to as a first bypass port 114a, and a bypass port located at a site that accounts for 20% of the maximum volume will be referred to as a second bypass port 114a. Notated as bypass port 114b, both bypass ports 11
4a and 114b are collectively referred to as the bypass port 11
Notation 4

Incidentally, in the scroll compressor, as shown in FIG. 3, the working chamber Vc is swirled from the outer side to the inner side of the spiral of the tooth portions 104a and 105b while turning the orbiting scroll 105, as shown in FIG. Since the volume is reduced, the first bypass port 114a is located on the spiral outer side of the second bypass port 114b.

When the shaft 101 is rotated, the orbiting scroll 105 tends to rotate around the crank portion 101a. However, as shown in FIG. 2, a well-known rotation preventing mechanism 105c including a pin and a ring is provided. The orbiting scroll 105 does not rotate and the shaft 10
Orbit (revolve) around one.

As shown in FIGS. 2 and 4, a guide cylinder bore (cylindrical hole) 115 extending in a straight line is formed in the end plate portion 104b, and the guide cylinder bore (hereinafter, abbreviated as cylinder) is formed. .) 115, a spool valve element (hereinafter, abbreviated as spool) 116 for opening and closing the bypass port 114 is slidably disposed.

The spool 116 is provided with the cylinder 1
The first to third valve portions 115a to 115c for opening and closing the first and second bypass ports 114a and 114b having outer dimensions substantially equal to the inner diameter of the first and second bypass ports 15, and bypass having an outer dimension smaller than the inner diameter of the cylinder 115. Rod portions 116d and 11 forming a passage for the refrigerant flowing out of the port 114
6e are formed.

Incidentally, 117 a to 117 c are bypass passages for guiding the refrigerant flowing out of the bypass port 114 to the suction chamber 106.

By the way, one end of the spool 116 in the sliding direction (the direction of the arrow in FIG. 2) (in this embodiment, the upper side of FIGS. A coil spring (elastic means) 118f that exerts an elastic force for pressing the pressure 116 is provided, and the suction pressure (pressure in the suction chamber 106) Ps of the compression mechanism Cp acts via the bypass passages 117a and 117c. ing. Hereinafter, the elastic force Fs and the suction pressure P of the coil spring 118f acting on one end of the spool 116 in the sliding direction will be described.
The force due to s is called the valve opening force.

On the other hand, at the other end of the spool 116 in the sliding direction (the lower side of FIGS. 2 and 4 in this embodiment), the discharge pressure Pd of the compression mechanism Cp is reduced and adjusted as shown in FIG. Pressure adjusting means 118 is provided for causing the adjusted pressure (hereinafter, this adjusted pressure is referred to as control pressure Pc) to be applied to the other end of the spool 116 in the sliding direction.

Hereinafter, the other end of the spool 116 in the sliding direction (the space 119 in which the control pressure Pc is introduced) is referred to as a control pressure chamber 119, and the control pressure acting on the other end of the spool 116 in the sliding direction. The force due to Pc is called a valve closing force.

The pressure adjusting means 118 is provided in the suction chamber 10.
First and second control passages 118a and 118b for communicating the pressure control chamber 6 with the control pressure chamber 119, and a first solenoid valve (first valve means) 118c for opening and closing the first control passage 118a and a second for opening and closing the second control passage 118b. 2 solenoid valve (second valve means) 118d
The control pressure chamber is provided only when the pressure difference between the suction chamber 106 and the control pressure chamber 119 provided in the second control passage 118b is equal to or higher than a predetermined pressure (hereinafter, this pressure is referred to as a set pressure difference). And a differential pressure valve 118e for flowing (releasing) the refrigerant in the suction chamber 119 to the suction chamber 106 side.

The first solenoid valve 118c is a non-energized open (normally open) type solenoid valve.
Reference numeral 18d denotes a normally closed solenoid valve when not energized.

The differential pressure valve 118e includes a spherical valve body for opening and closing the second control passage 118b and a coil spring (elastic member) for applying an elastic force to the spherical valve body in a direction to close the second control passage 118b. It is a well-known structure.

Numeral 120 denotes a stopper which regulates the maximum displacement of the spool 116 and also serves as a lid (plug) for closing one end of the cylinder 115. Numeral 121 denotes a predetermined pressure loss between the discharge chamber 107 and the control pressure chamber 119. Is a fixed diaphragm (diaphragm means) that communicates with the diaphragm.

Next, the characteristic operation of the compressor 100 will be described with reference to FIG.

1. Operation at minimum capacity (about 20%) (Fig. 5
(See (a)) The energization of the first and second solenoid valves 118c and 118d is cut off,
The first control passage 118a is communicated, and the second control passage 118b is closed.

As a result, the control pressure Pc in the control pressure chamber 119 becomes the suction pressure Ps.
The valve opening force exceeds the valve closing force due to the elastic force Fs of f, and the spool 116 slides and displaces in the direction of the elastic force Fs until the spool 116 collides with the stopper 120.

In this state, since the first and second bypass ports 114a and 114b are configured to be opened, the discharge capacity of the compressor 100 (compression mechanism Cp) is about 20% of the maximum capacity.

2. During operation of intermediate capacity (about 50%) (Fig. 5
(See (b)) By energizing the first and second solenoid valves 118c and 118d, the first control passage 118a is closed and the second control passage 118 is closed.
b.

As a result, the valve closing force is increased by an amount corresponding to the set differential pressure of the differential pressure regulating valve 118e as compared with the operation at the time of the minimum capacity operation. Sliding displacement occurs.

In this state, since the first bypass port 114a is opened and the second bypass port 114b is closed, the discharge capacity of the compressor 100 (compression mechanism Cp) is reduced to about 50 at the maximum. %.

3. When operating at maximum capacity (100%) (Fig. 5
(Refer to (c).) While energizing the first solenoid valve 118c, the second solenoid valve 1
The first and second control passages 118a and 118b are closed by cutting off the current supply to 18d.

As a result, the control pressure Pc becomes the discharge pressure Pd, so that the valve closing force exceeds the valve opening force, and the coil spring 1
18f is compressed by the elastic force Fs
Sliding displacement in the direction opposite to the direction of

In this state, since the first and second bypass ports 114a and 114b are configured to be closed, the discharge capacity of the compressor 100 (compression mechanism Cp) becomes
Maximum capacity.

Next, the features of this embodiment will be described.

According to the present embodiment, the coil spring 1
Since the spool 116 is moved by balancing the elastic force Fs of 18f with the control pressure Pc obtained by reducing and adjusting the discharge pressure Pd, the elastic force Fs is (sufficiently) greater than the force due to the maximum pressure of the control pressure Pc (suction pressure Ps). If so, the spool 116 can be moved without being affected by the heat load of the cycle.

Therefore, when the load on the engine 500 is large, such as during acceleration or climbing a hill, the pressure adjusting means 118 (first and second solenoid valves 118c, 118d) is operated to reduce the displacement of the compressor 100. Then, the engine 50
It is possible to quickly reduce and change the discharge capacity in response to a load change of zero. As a result, it is possible to prevent the discharge capacity from being excessively reduced while sufficiently improving the acceleration performance and the vehicle fuel efficiency.

When the discharge capacity of the compressor 100 is reduced (for example, during an intermediate capacity operation), the control pressure Pc
Is a pressure having a set differential pressure (approximately 0.2 MPa in the present embodiment) with respect to the suction pressure Ps, so that the pressure is not influenced by the fluctuation of the suction pressure Ps, that is, the heat load of the cycle.
The spool 116 can be operated with good responsiveness to the operation of the pressure adjusting means 118.

If at least the first solenoid valve 118c is opened while the compressor 100 is stopped, the compressor 100 starts operating in the minimum capacity operation state when the compressor 100 starts. Shock (large torque fluctuation generated in engine 500) generated at the time of starting 100 can be reduced.

Further, since the discharge capacity of the compressor 100 is controlled in three stages (20%, 50%, 100%), it is possible to finely control the load of the engine 500 as well as the heat load of the cycle. It is possible to control the discharge capacity.

Further, as shown in FIG. 4, by arranging the bypass ports 114 substantially in a straight line, a plurality of bypass ports 114 can be opened and closed by one spool 116. Therefore, the structure of the opening / closing mechanism of the bypass port 114 can be simplified while suppressing an increase in the number of parts.

In this embodiment, the first solenoid valve 118
Although c is a normally open type and the second solenoid valve 118d is a normally closed type, the present embodiment is not limited to this.

(Second Embodiment) In the present embodiment, as shown in FIG. 6, the stopper 120 located at the other end in the sliding direction of the spool 116 can be slid in the same direction as the spool 116. Thus, the maximum displacement width of the spool 116 is changed to control the discharge capacity in three stages.

Hereinafter, the features of this embodiment will be described with reference to FIG. Except for the pressure adjusting means for controlling the movement (sliding) of the spool 116, the configuration is the same as that of the first embodiment, and the description of the overall structure of the compressor 100 will be omitted.

One end of the spool 116 in the sliding direction (in the direction of the arrow in FIG. 6) (in this embodiment, the upper side in FIG. 6) is moved toward the other end in the sliding direction of the spool 116.
A coil spring (elastic means) 122 which exerts an elastic force to press the air is provided, and the bypass passage 1
The suction pressure Ps acts via 17a and 117c.

On the other hand, the other end of the spool 116 in the sliding direction (the lower side in FIG. 6 in this embodiment) is switched between the discharge pressure Pd and the suction pressure Ps, and the switched control pressure is applied to the spool 116 in the sliding direction. A first pressure adjusting means 123 that acts on the other end in the moving direction is provided. Hereinafter, the pressure supplied to the other end of the spool 116 in the sliding direction by the first pressure adjusting means 123 is referred to as a first control pressure Pc1, and the first control pressure Pc1
The space 124 in which c1 acts is referred to as a first control pressure chamber 124. Incidentally, the first control pressure chamber 124 includes a cylinder 115, a spool 116, and a stopper 120, as is apparent from FIG.

Here, the first pressure adjusting means 123 has a first fixed throttle 125 for generating a predetermined pressure loss, and has a refrigerant passage 126 for communicating the discharge chamber 107 with the first control pressure chamber 124. The first control pressure chamber 124 and the suction chamber 106 communicate with each other, and include a normally open third electromagnetic valve 128 that opens and closes a refrigerant passage 127.

Reference numeral 129 denotes a second pressure adjusting means for switching the discharge pressure Pd and the suction pressure Ps on the side of the stopper 120 opposite to the spool 116 and applying the control pressure. Hereinafter, the pressure supplied by the second pressure adjusting means 129 to the side of the stopper 120 opposite to the spool 116 is referred to as a second control pressure Pc2, and the space 130 on which the second control pressure Pc2 acts is subjected to the second control pressure. It is described as a pressure chamber 130.

Here, the second pressure adjusting means 129 has a second fixed throttle 131 for generating a predetermined pressure loss, and has a refrigerant passage 132 for communicating the discharge chamber 107 with the second control pressure chamber 130. The second control valve 130 includes a normally open fourth solenoid valve 134 that opens and closes a refrigerant passage 133 that connects the second control pressure chamber 130 and the suction chamber 106.

Next, the characteristic operation of the compressor 100 will be described with reference to FIG.

1. Operation at minimum capacity (about 20%) (Fig. 6
(See (a).) The energization of the third and fourth solenoid valves 128 and 134 is interrupted, and the first and second control pressures Pc1 and Pc2 are set to the suction pressure Ps.

Thus, while the spool 116 collides with the stopper 120 due to the elastic force Fs of the coil spring 122, the stopper 120 slides and displaces in the direction of the elastic force Fs until the stopper 120 collides with the step 115a of the cylinder 115. Here, the stepped portion 115a constitutes stopper means for restricting the maximum displacement of the stopper 120.

In this state, since the first and second bypass ports 114a and 114b are configured to be opened, the discharge capacity of the compressor 100 (compression mechanism Cp) is about 20% of the maximum capacity.

2. During operation of intermediate capacity (about 50%) (Fig. 6
(See (b).) By interrupting the energization of the third solenoid valve 128 and energizing the fourth solenoid valve, the first control pressure Pc1 is set to the suction pressure Ps,
The second control pressure Pc2 is defined as a discharge pressure Pd.

As a result, the stopper 120 has the elastic force Fs
The spool 166 moves to one end in the sliding direction of the spool 166 so as to compress the coil spring 122 in opposition to
When the second bypass port 114b is closed, the discharge capacity of the compressor 100 (compression mechanism Cp) is reduced to about 5 at the maximum.
0%.

3. When operating at maximum capacity (100%) (Fig. 6
(See (c).) The third and fourth solenoid valves 128 and 134 are energized, and the first and second control pressures Pc1 and Pc2 are set to the discharge pressure Pd.

As a result, the spool 116 is slid and displaced in the direction opposite to the direction of the elastic force Fs so as to compress and contract the coil spring 122, so that the first and second bypass ports 114a and 114b are closed and the compressor 100 (compressor). Mechanism C
The discharge capacity of p) is the maximum capacity.

As described in the first embodiment, if the discharge capacity of the compressor 100 is controlled in accordance with the load of the engine 500, the discharge capacity may be excessively improved while sufficiently improving the acceleration performance and the fuel efficiency of the vehicle. It can be prevented from being lowered.

(Third Embodiment) In this embodiment, as shown in FIG. 7, the first control pressure Pc1 is applied to the first pressure adjusting means 123.
Refrigerant passages (first passages) 126 and 127 for guiding the second control pressure to the second pressure adjusting means 129 and refrigerant passages (second passages) 132 and 133 for guiding the second control pressure are provided between the rear housing 151 and the fixed scroll 104. The gasket 150 is provided substantially in parallel with the gasket 150 sandwiched therebetween.

That is, as shown in FIGS. 7 and 8, grooves forming the refrigerant passages 126 and 127 are formed in the surface of the end plate portion 104b of the fixed scroll 104 on the rear housing 151 side. End plate 10
The grooves forming the refrigerant passages 132 and 133 are formed on the surface on the 4b side, and the opening sides of the groove of the end plate portion 104b and the groove of the rear housing 151 are closed by a gasket 150.

The gasket 150 seals the rear housing 151 and the fixed scroll 104 without any gap. In this embodiment, the gasket 150 is formed by coating both surfaces of a metal with a resin such as rubber. is there.

Next, the features of this embodiment will be described.

By the way, the pulsation of the refrigerant discharged from the working chamber Vc is smoothed in the discharge chamber 107. In order to sufficiently smooth the pulsation, the capacity of the discharge chamber 107 needs to be sufficiently large. .

Here, temporarily, the refrigerant passages 126 and 127 (hereinafter, this refrigerant passage is referred to as a first refrigerant passage 126).
And the refrigerant passages 132 and 133 (hereinafter, this refrigerant passage is referred to as a second
It is described as a refrigerant passage 132. ) And the rear housing 151 and the fixed scroll 104 (end plate portion 104b).
Formed on either side of the two
6 and 132 are arranged in parallel with each other in the axial direction of the compressor (parallel to the direction of the paper surface of FIG. 8), so that the volume of the discharge chamber 107 may be reduced.

On the other hand, according to the present embodiment, the first and second refrigerant passages 126 and 132 are provided substantially parallel to each other with the first and second refrigerant passages 126 and 132 defined by the gasket 150.
Since the two refrigerant passages 126 and 132 are arranged in series in the axial direction of the compressor, it is possible to prevent the capacity of the discharge chamber 107 from being reduced. Therefore, it is possible to sufficiently improve the acceleration performance and the vehicle fuel efficiency while sufficiently smoothing the pressure pulsation, and to prevent the discharge capacity from being excessively reduced.

In this embodiment, the third and fourth solenoid valves 1
28, 134 are disposed between the front housing 102 and the rear housing 151, and the refrigerant passages 127, 1
33 is provided in the rear housing 151, but as shown in FIG. 9, third and fourth solenoid valves 128 and 134 are provided between the front housing 102 and the fixed scroll 104,
In addition, the refrigerant passages 127 and 133 are
And third and fourth solenoid valves 128 and 134 and refrigerant passages 127 and 13 as shown in FIG.
3 may be provided in the rear housing 151.

(Fourth Embodiment) In the present embodiment, as shown in FIG.
A coil spring (elastic means) 140 for applying an elastic force to the stopper 120 to press the stopper 120 toward the spool 116 is provided in the second control chamber 130.

As a result, the stopper 120 can be prevented from vibrating (rattle) in the first control chamber 124 (space 124) due to the vibration of the engine 500 or the vehicle. Can be prevented.

As apparent from FIGS. 11A and 11B, during the minimum capacity operation and the intermediate capacity operation, the stopper 120 is sandwiched between the spool 116 and the coil spring 140. As a result, during the maximum capacity operation, the stopper 120 is sandwiched between the stepped portion 115a and the coil screw 140 to suppress the vibration.

(Other Embodiments) In the first embodiment,
Although the second solenoid valve 118d was closed during the minimum capacity operation,
In this state, since the first solenoid valve 118c is open,
There is no practical problem in controlling the second solenoid valve 118d to open.

In the above-described embodiment, the load of the engine 500 is detected by detecting the opening of the throttle valve. However, the load of the engine 500 is determined based on a change in the number of revolutions of the engine 500 and other parameters such as the suction negative pressure. May be detected.

Further, the compressor according to the present invention has a working chamber Vc
Can be applied to a type of compressor that moves while expanding and contracting its volume,
The present invention is also applicable to rolling piston type and vane type compressors.

In the above embodiment, the pressure control means (electromagnetic valve or the like) is built in the compressor. However, the pressure control means (electromagnetic valve or the like) may be externally attached to the fixed scroll 104.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of a refrigeration cycle.

FIG. 2 is a sectional view of the compressor according to the first embodiment of the present invention.

FIG. 3 is an explanatory diagram showing the operation of the orbiting scroll.

FIG. 4 is a sectional view taken along line AA of FIG. 1;

FIG. 5 is an explanatory diagram showing an operation of a spool in the compressor according to the first embodiment of the present invention.

FIG. 6 is an explanatory diagram showing an operation of a spool in a compressor according to a second embodiment of the present invention.

FIG. 7 is a sectional view of a compressor according to a third embodiment of the present invention.

FIG. 8 is a sectional view taken along line BB of FIG. 7;

FIG. 9 is a sectional view of a compressor according to a modification of the third embodiment of the present invention.

FIG. 10 is a sectional view of a compressor according to a modification of the third embodiment of the present invention.

FIG. 11 is an explanatory diagram showing an operation of a spool in a compressor according to a fourth embodiment of the present invention.

[Explanation of symbols]

101: shaft, 104: fixed scroll, 105:
Orbiting scroll, 114: bypass port, 118: pressure adjusting means, 118c: first solenoid valve, 118d: second solenoid valve, 118e: differential pressure valve, 118f: coil spring (elastic means).

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Takashi Inoue 14 Iwatani, Shimowasukamachi, Nishio City, Aichi Prefecture Inside the Japan Automobile Parts Research Institute (72) Inventor Shigeki Iwanami 1-1-1, Showacho, Kariya City, Aichi Prefecture Shares In company DENSO (72) Inventor Haruo Kamiya 1-1-1, Showa-cho, Kariya-shi, Aichi F-term in DENSO Corporation (reference) 3H039 AA02 AA12 BB12 BB22 CC02 CC29 CC30 CC34 CC40 CC46

Claims (8)

[Claims] An orbiting scroll (105) having a fixed scroll (104) and an orbiting scroll (105);
5) is rotated with respect to the fixed scroll (104), so that at least one of a compression mechanism (Cp) for expanding and reducing a working chamber (Vc) for sucking and compressing a fluid, and the working chamber (Vc) during a compression stroke. Working chamber in two states (V
c) a variable displacement scroll compressor comprising a plurality of bypass holes (114) for communicating the suction side of the compression mechanism (Cp) with the suction side, and a valve element (116) for opening and closing the bypass holes (114). In the valve body (116), elastic means (118f, 122) for applying an elastic force to one end side in the movable direction, and the discharge pressure of the compression mechanism (Cp) were reduced and adjusted. Pressure adjusting means (118, 12) for applying the adjustment pressure to the other end of the valve body (116) in the movable direction.
3, 129). 2. The suction pressure of the compression mechanism (Cp) acts on one end of the valve element (116) in the movable direction in addition to the elastic force. 2. The variable displacement scroll compressor according to claim 1, wherein the pressure can be reduced and adjusted so that the adjusted pressure has a predetermined pressure difference from the suction pressure. 3. The variable displacement scroll compressor (100) according to claim 1 or 2, wherein the variable displacement scroll compressor (100) operates by receiving a driving force from a vehicle driving source (500). A radiator (200) for cooling the refrigerant discharged from the radiator (200); a decompressor (300) for decompressing the refrigerant flowing out of the radiator (200); and evaporating the refrigerant decompressed by the decompressor (300). An evaporator (400) for causing the evaporated refrigerant to flow toward the suction side of the variable capacity scroll compressor (100); and a drive load detecting means for detecting a drive load of the vehicle drive source (500). And (600), when the driving load detected by the driving load detecting means (600) is equal to or more than a predetermined load, the pressure adjusting means (118, 123, 129) is operated to Vehicle refrigeration cycle, characterized by a control means (700) to reduce the discharge capacity of the variable capacity scroll compressor (100). 4. An orbiting scroll (10) having a fixed scroll (104) and an orbiting scroll (105).
5) is rotated with respect to the fixed scroll (104), so that at least one of a compression mechanism (Cp) for expanding and reducing a working chamber (Vc) for sucking and compressing a fluid, and the working chamber (Vc) during a compression stroke. Working chamber in two states (V
c) a variable displacement scroll compressor comprising a plurality of bypass holes (114) for communicating the suction side of the compression mechanism (Cp) with the suction side, and a valve element (116) for opening and closing the bypass holes (114). An elastic means (122) for applying an elastic force to one end of the valve element (116) in the movable direction; and a compression mechanism provided to the other end of the valve element (116) in the movable direction. (Cp) discharge pressure and the compression mechanism (Cp)
Pressure adjusting means (1
23) and the other end of the valve element (116) in the movable direction is disposed so as to be displaceable in a direction parallel to the movable direction of the valve element (116), and regulates the movable range of the valve element (116). And a second pressure adjusting means (129) for switching the discharge pressure and the suction pressure to act on the opposite side of the stopper (120) from the valve element (116). Characteristic variable capacity scroll compressor. 5. An orbiting scroll (10) having a fixed scroll (104) and an orbiting scroll (105).
5) is rotated with respect to the fixed scroll (104), so that at least a compression mechanism (Cp) for expanding or reducing a working chamber (Vc) for sucking and compressing a fluid, and the working chamber (Vc) during a compression stroke. Working chamber in two states (V
c) and a plurality of bypass holes (114) for communicating the suction side of the compression mechanism (Cp) with the suction holes (11).
4) is fixed to the fixed scroll (104) via the valve body (116) for opening and closing, and the fixed scroll (104) and the gasket (150), and the working chamber (V
c) a discharge chamber (10) for smoothing the pulsation of the fluid discharged from
7) A variable displacement scroll compressor including a rear housing (151) that constitutes 7), wherein: an elastic means (122) for applying an elastic force to one end of the valve body (116) in a movable direction thereof; Discharge pressure of the compression mechanism (Cp) and the compression mechanism (Cp) are provided on the other end of the valve body (116) in the movable direction.
Pressure adjusting means (1
23), and the other end of the valve body (116) in the movable direction is disposed so as to be displaceable in a direction parallel to the movable direction of the valve body (116), and regulates the movable range of the valve body (116). A stopper (120) that performs the operation, and a second pressure adjusting unit (129) that switches and operates the discharge pressure and the suction pressure on a side of the stopper (120) opposite to the valve element (116); A first passage (126, 127) for introducing pressure to the first pressure adjusting means (123);
9) A variable displacement scroll-type compressor characterized in that second passages (132, 133) for introducing pressure to the gasket (150) are provided substantially in parallel with each other and defined by the gasket (150). 6. An orbiting scroll (10) having a fixed scroll (104) and an orbiting scroll (105).
5) is rotated with respect to the fixed scroll (104), so that at least one of a compression mechanism (Cp) for expanding and reducing a working chamber (Vc) for sucking and compressing a fluid, and the working chamber (Vc) during a compression stroke. Working chamber in two states (V
c) a variable displacement scroll compressor comprising a plurality of bypass holes (114) for communicating the suction side of the compression mechanism (Cp) with the suction side, and a valve element (116) for opening and closing the bypass holes (114). An elastic means (122) for applying an elastic force to one end of the valve element (116) in the movable direction; and a compression mechanism provided to the other end of the valve element (116) in the movable direction. (Cp) discharge pressure and the compression mechanism (Cp)
Pressure adjusting means (1
23) and the other end of the valve element (116) in the movable direction is disposed so as to be displaceable in a direction parallel to the movable direction of the valve element (116), and regulates the movable range of the valve element (116). A second pressure adjusting means (129) for switching the discharge pressure and the suction pressure to act on the opposite side of the stopper (120) from the valve element (116); And a resilient means (140) for applying an elastic force for pressing the resilient member (120) toward the valve body (116). 7. The variable displacement scroll type compressor (100) according to claim 4, wherein the variable displacement scroll type compressor (100) operates by receiving a driving force from a vehicle driving source (500). A radiator (200) for cooling the refrigerant discharged from the compressor (100), a decompressor (300) for reducing the pressure of the refrigerant flowing out of the radiator (200), and a pressure reduced by the decompressor (300). An evaporator (400) for evaporating the refrigerant and causing the evaporated refrigerant to flow toward the suction side of the variable capacity scroll compressor (100), and a drive load of the vehicle driving source (500) is detected. A first and second pressure adjusting means (123, 129) when the driving load detected by the driving load detecting means (600) exceeds a predetermined load. Of vehicle refrigeration cycle, characterized by a control means (700) to reduce the discharge capacity of the by actuating at least one variable displacement scroll type compressor (100). 8. A compression mechanism (Cp) having a fixed member (104) and a movable member (105) movable with respect to the fixed member (104) to expand and contract a working chamber (Vc) for sucking and compressing a fluid. A plurality of bypass holes (114) for communicating between at least two types of working chambers (Vc) of the working chambers (Vc) during the compression stroke and the suction side of the compression mechanism (Cp); A variable displacement compressor having a valve element (116) for opening and closing a hole (114), wherein elastic means (118f, 122) for applying an elastic force to one end of the valve element (116) in its movable direction. Pressure adjusting means (118, 12) for reducing the discharge pressure of the compression mechanism (Cp) and applying the adjusted pressure to the other end of the valve element (116) in the movable direction.
3, 129).