JPH11210661A - Variable capacity type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable capacity type compressor in which the communicating direction of a coolant is never changed regardless of the rotating direction of the compressor. SOLUTION: A suction port 130 is communicated to an operation chamber V in the condition to expand the volume when a rotor 123 is rotated regularly, a first discharge port 151 is communicated to the operation chamber V in the condition to reduce the volume when the rotor is rotated regularly, while a second discharge port 152 is communicated to the operation chamber in the condition to expand the volume when the rotor is rotated regularly. Consequently, the communicating direction of a coolant can be made the same regardless of the rotating direction of a compressor.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement type compression system capable of changing a displacement, and a so-called refrigeration cycle for a so-called hybrid vehicle running with an engine (internal combustion engine) and an electric motor. It is effective to apply to In addition, the hybrid vehicle referred to in the present specification includes not only a hybrid vehicle that travels by switching between an engine and an electric motor, but also a hybrid vehicle that uses an engine only for power generation without using the engine for traveling and performs vehicle traveling only with an electric motor. Including.

[0002]

2. Description of the Related Art In the invention described in Japanese Patent Application Laid-Open No. 63-50693, in a rolling piston type compressor, the rolling piston is rotated in one direction (forward rotation) so that the discharge capacity is maximized. On the other hand, the variable displacement compressor is configured such that the displacement is minimized by rotating (reversely rotating) the rolling piston in another direction.

[0003]

However, in the variable displacement compressor described in the above publication, the fluid flows from the suction port and discharges from the discharge port during normal rotation.
At the time of reverse rotation, the fluid flows in from the discharge port and is discharged from the suction port, so that the flow direction of the fluid is opposite between the forward rotation and the reverse rotation.

For this reason, when the variable displacement compressor described in the above publication is applied to a refrigeration cycle, it is possible to change the discharge capacity during air conditioning operation only for cooling operation or heating operation. Can not. Also, if any air conditioning operation is being performed, it is necessary to provide a switching valve such as a four-way valve to switch the passage to change the discharge capacity, so that the number of components of the refrigeration cycle increases. And the production cost of the refrigeration cycle rises.

[0005] In view of the above, it is an object of the present invention to provide a variable displacement compressor in which the direction of fluid flow does not change regardless of the direction of rotation of the compressor.

[0006]

The present invention uses the following technical means to achieve the above object. Claim 1
In the invention described in Item 4, the suction port (130) communicates with the working chamber (V) whose volume increases when the shaft (120) rotates forward, and the first discharge port (151).
Communicates with the working chamber (V) whose volume decreases when the shaft (120) rotates forward, and the second discharge port (152) communicates with the working chamber (V) when the shaft (120) rotates forward. It is characterized in that it communicates with the working chamber (V) in an expanding state.

Accordingly, the discharge capacity when the shaft (120) rotates forward matches the volume when the volume of the working chamber (V) is maximized, and the fluid is discharged from the first discharge port (151). Will be done. On the other hand, when the shaft (120) rotates in the reverse direction, when the volume of the working chamber (V) is reduced, fluid is sucked and the second discharge port (1) is sucked.
52). Therefore, the discharge capacity when the shaft (120) is reversed is reduced by the shaft (1).
20) can be made smaller than the discharge capacity at the time of forward rotation, and the direction of fluid flow can be constant regardless of the direction of rotation of the shaft (120).

[0008] Forward rotation means rotation in one of the rotation directions of the shaft (120), and reverse rotation means rotation in the opposite direction to normal rotation. According to the second aspect of the present invention, when the shaft (120) rotates, the communication port (14) opening to the working chamber (V) whose volume is increasing.
1, 142) and the communication port (14
A check valve (144) for preventing the fluid from flowing back from the communication ports (141, 142) to the suction port (130) is provided in the passage (143) extending from the communication ports (141, 142) to the suction port (130). It is characterized by the following.

Thus, when the volume of the working chamber (V) increases, the inside of the working chamber (V) can be prevented from becoming negative pressure, so that the variable displacement compressor performs unnecessary work. Can be prevented. According to the fifth aspect of the present invention, when the shaft (120) is rotated forward, the shaft (120) is rotated by obtaining driving force from the engine, and the shaft (12) is rotated.
When the rotation of the shaft (120) is performed in reverse, the driving force is obtained from the electric motor (510) to rotate the shaft (120).

Thus, the driving force (torque) when driving the shaft (120) by the electric motor (510) can be reduced, so that the electric motor (510) can be prevented from being enlarged. In addition, the code | symbol in the parenthesis of each said means shows the correspondence with the concrete means of embodiment mentioned later.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
Variable displacement compressor according to the present invention (hereinafter abbreviated as compressor)
100 is applied to a refrigeration cycle for a hybrid vehicle, and FIG. 1 is a schematic diagram of a refrigeration cycle.

In FIG. 1, reference numeral 200 denotes a condenser (radiator) for condensing a refrigerant (fluid) discharged from the compressor 100;
A decompressor 300 decompresses the refrigerant flowing out of the condenser 200, and an evaporator 400 evaporates the liquid-phase refrigerant depressurized by the depressurizer 300. Next, the compressor 100 will be described.

FIG. 2 is an axial sectional view of the compressor 100. In FIG. 2, reference numeral 110 denotes an aluminum housing. This housing 110 is a front housing 11
1. Middle housing 112, cylinder housing 11
3 and a rear housing 114, and these housings 111 to 114 are fixed by bolts (not shown).

Reference numeral 120 denotes a shaft which rotates by receiving a driving force from an engine (not shown) for driving the vehicle. One end of the shaft 120 (the front housing 111 side)
, A spline 121 to which a pulley (not shown) to which driving force from the engine is transmitted and an electromagnetic clutch (not shown) are mounted. In addition, a rotor 123 integrally formed with the shaft 120 is provided in a space 122 formed by the middle housing 112, the cylinder housing 113, and the rear housing 114. As shown in FIG. The rotor 1 is slidable in the radial direction of the rotor 123 (possible to appear and disappear).
Plate-like vanes 124a, 124b inserted in
(Hereinafter, both vanes 124a and 124b are collectively referred to as vanes 124.), and are disposed with their ends in contact with the inner wall 113a of the space 122 (cylinder housing 113).

The diameter of the rotor 123 is determined by the space 122
And a part of the rotor 123 is in contact with the inner wall 113a of the cylinder housing 113, so that the space 122 is divided into five working chambers V1 to V5 including a part partitioned by the vane 124. Have been.
Therefore, when the rotor 123 (the shaft 120) rotates, each of the working chambers V1 to V5 moves in the direction of rotation of the rotor 123 while increasing or decreasing the volume.

More specifically, when the rotor 123 rotates in one direction shown in FIG. 3 (hereinafter, the state of rotation in this direction is referred to as forward rotation), the working chamber V1 expands its volume. , Moves to the position of the working chamber V2 and the position of the working chamber V3. Thereafter, the working chamber V1 moves to the position of the working chamber V4 and the position of the working chamber V5 while reducing its volume.

Conversely, when the rotor 123 rotates in the other direction shown in FIG. 4 (hereinafter, this state of rotation is referred to as reverse rotation), the working chamber V5 increases its volume while maintaining its working volume. And the working chamber V3. Thereafter, the working chamber V5 moves to the position of the working chamber V2 and the position of the working chamber V1 while reducing its volume.

The middle housing 112 has an open suction port 130 for supplying the working chamber V with the refrigerant drawn into the working chambers V1 to V5 (hereinafter, these are collectively referred to as the working chamber V). The suction port 130 is formed so as to communicate with the working chamber V (in this embodiment, the position of the working chamber V2) whose volume is increasing when the rotor 123 (the shaft 120) rotates forward. Have been. The suction port 130 communicates with a suction chamber 131 (see FIG. 2) formed in the front housing 111.
This suction chamber 131 is connected to the outlet side of the evaporator 400.

The middle housing 112 has, in addition to the suction port 130, first and second communication ports 141 and 142 communicating with the suction port 130 side.
The first communication port 141 is opened so as to communicate with the working chamber V (the position of the working chamber V1 in this embodiment) whose volume increases when the rotor 123 rotates forward, and the second communication port 142 is opened. Is the working chamber V in a state in which the volume increases when the rotor 123 rotates in the reverse direction (in this embodiment, the working chamber V
(Position 5)).

In the passage 143 extending from the communication ports 141 and 142 to the suction port 130, a check valve 144 for preventing the refrigerant from flowing back from the communication ports 141 and 142 to the suction port 130 is provided. ing. A discharge chamber 150 connected to the inlet side of the condenser 200 is formed in the cylinder housing 113, and first and second discharge ports 151 for communicating the discharge chamber 150 with the space 122 (working chamber V). , 152 are formed. The first discharge port 151 is connected to the rotor 123
The opening is opened so as to communicate with the working chamber (the position of the working chamber V5 in this embodiment) whose volume is reduced when the (shaft 120) rotates forward, and the second discharge port 152 is connected to the rotor 123 (shaft). 120) is open so as to communicate with the working chamber (in this embodiment, the position of the working chamber V1) whose volume is increasing when it rotates forward.

Incidentally, reference numeral 153 denotes both discharge ports 151,
This is a discharge valve for preventing the refrigerant from flowing back from the discharge chamber 150 to the working chamber V via the 152. Also, in FIG.
Reference numeral 120a is a bearing that rotatably supports the shaft 120. Next, the operation and characteristics of the compressor 100 according to the present embodiment will be described. 1. When the rotor 123 rotates forward (maximum displacement operation) When the rotor 123 rotates forward, as shown in FIG. 3, the working chamber V1 expands its volume to suck the refrigerant from the suction port 130, It moves to the position of. Therefore, the maximum suction amount is the volume of the working chamber V3 having the maximum volume.

Thereafter, the working chamber V1 compresses the refrigerant while reducing its volume. When the refrigerant reaches the position of the working chamber V5, the refrigerant is discharged from the first discharge port 151.
When the working chamber V1 moves to the position of the working chamber V2,
Although the volume is increased, since the refrigerant is supplied from the first communication port 141, it is possible to prevent the working chamber V1 from becoming a negative pressure. Therefore, it is possible to prevent the compressor 100 from performing unnecessary work.

2. When the rotor 123 is rotated in the reverse direction (minimum capacity operation) When the rotor 123 is rotated in the reverse direction, the working chamber V5 expands its volume and sucks the refrigerant from the second communication port 142 as shown in FIG. While moving to the position of the working chamber V3. Accordingly, as in the case of the forward rotation, when the volume of the working chamber V5 is increased, it is possible to prevent the working chamber V5 from becoming a negative pressure, thereby preventing the compressor 100 from performing unnecessary work. it can.

Thereafter, the working chamber V1 is reduced in volume. However, since the working chamber V communicates with the suction port 130, the working chamber V1 is returned to the suction chamber 131 without compressing the refrigerant. The refrigerant moves to the position V1 and the refrigerant is discharged from the second discharge port 152. Therefore, the amount of refrigerant finally sucked into the working chamber V1 becomes the volume of the working chamber V1, and the operation is the minimum capacity operation.

As described above, according to the compressor 100 of the present embodiment, the second discharge port 152 is newly provided without providing a switching valve such as a four-way valve, and the like. It is possible to prevent the flow direction of the refrigerant from changing regardless of the rotation direction of the compressor 100 (the shaft 120). As a result, an increase in the production cost of the refrigeration cycle can be prevented.

In this embodiment, the second communication port 1
Although 42 is provided only at the position of the working chamber V5, the number and size of the second communication ports 142 are not limited to this, and are appropriately selected according to the capacity of the compressor 100. (Second Embodiment) In this embodiment, as shown in FIG. 5, a compressor 100 and an electric motor 510 are integrated (hereinafter, the integrated device is referred to as a compression device 500).
It is.

When the compressor 500 rotates forward (at the time of maximum capacity operation), the shaft 1 is driven by the engine.
When the compressor 100 is operated by rotating 20 and the compressor 100 is rotated in reverse (at the time of minimum capacity operation), the shaft 120 is rotated by the electric motor 510 to operate the compressor 100. By the way, the driving force (torque) obtained from the electric motor 510 and the driving force (torque) obtained from the engine
If it is attempted to make the same, the size of the electric motor 510 will be increased.

On the other hand, when the compressor 100 is operated by the electric motor 510 as in the present embodiment,
When the motor is driven in the minimum capacity operation state by reversing,
Since the required driving force can be reduced at 0, it is possible to prevent the electric motor 510 from increasing in size. In order to obtain the same refrigerating capacity during the minimum capacity operation as during the maximum capacity operation (when the compressor 100 is operated by the engine), the rotational speed of the electric motor 510 may be increased.

In the above embodiment, the rotor 1
Although the space 122 is partitioned into a plurality of working chambers V by the 23 and the vanes 124, and a movable member that expands and contracts the volume of the working chambers V in conjunction with the rotation of the shaft 120, the present invention is not limited thereto. However, as shown in FIG.
Instead of 4, a rolling piston type compressor in which a movable member is constituted by a rolling piston 160 that rotates integrally with the shaft 120 in the space 122 may be used.

Further, the variable displacement compressor according to the present invention comprises:
The application is not limited to the hybrid vehicle, and can be applied to a vehicle that stops the engine when the vehicle stops (a so-called eco-run vehicle).

[Brief description of the drawings]

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

FIG. 2 is an axial sectional view of the variable displacement compressor according to the first embodiment.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a sectional view taken along line AA of FIG. 2;

FIG. 5 is an axial sectional view of the variable displacement compressor according to the first embodiment.

FIG. 6 is a sectional view of a variable displacement compressor according to a modification of the present invention.

[Explanation of symbols]

123 ... rotor, 124 ... vane, 130 ... suction port, 141 ... first communication port, 142 ... second communication port, 151 ... first discharge port, 152 ... second discharge port.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Takeshi Sakai 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside DENSO Corporation

Claims (5)

[Claims] 1. A housing (110); a shaft (120) rotatably disposed in the housing (110); and a space (12) formed in the housing (110).
2) movable within the chamber, and partitions the space (122) into a plurality of working chambers (V), and expands and contracts the volumes of the working chambers (V) in conjunction with the rotation of the shaft (120). A movable member (123, 124, 160); a suction port (130) for supplying a fluid sucked into the working chamber (V) to the working chamber (V) in the housing (110); First and second discharge ports (15) for discharging the fluid compressed in the working chamber (V) to the outside of the working chamber (V).
1, 152) and the two discharge ports (151, 15).
A discharge chamber (150) communicating with 2) is formed, and the suction port (130) is connected to the shaft (120).
When the cylinder rotates forward, the first discharge port (151) communicates with the working chamber (V) in a state where the volume is increasing, and the first discharge port (151) is connected to the shaft (12).
0) rotates forward when the volume is reduced, the second discharge port (152) communicates with the shaft (12).
The variable displacement compressor is characterized in that, when 0) rotates forward, it communicates with the working chamber (V) whose volume is increasing. 2. The housing (110) has an opening in the working chamber (V) in which the volume is expanding when the shaft (120) rotates, and the suction port (130). Communication port (14
1, 142) are formed, and a passage (143) from the communication ports (141, 142) to the suction port (130) side is provided from the communication ports (141, 142) to the suction port (130). The variable displacement compressor according to claim 1, wherein a check valve (144) for preventing a fluid from flowing backward is provided on the side. 3. The movable member has a rotor (123) that rotates integrally with the shaft (120) in the space (122), and a vane (124) that protrudes and retracts from the rotor (123). The variable displacement compressor according to claim 1, wherein the compressor is configured. 4. The moving member according to claim 1, wherein the movable member has a rolling piston (160) that rotates integrally with the shaft (120) in the space (122). 3. The variable displacement compressor according to claim 1. 5. A variable displacement compressor according to claim 1, wherein said compressor is applied to a compressor of a vehicle refrigeration cycle, and said shaft is driven by said engine when rotating forward. When the shaft (120) is rotated by obtaining force and the shaft (120) is rotated in reverse, the driving force is obtained from the electric motor (510) and the shaft (12) is rotated.
A compressor device characterized by rotating 0).