JPH10196568A - Compressor and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To control the capacity in plural stages in a double rotor type compressor where the discharge volumes of plural compressing elements are different from each other, by comprising a power saving means which comprises a shut- off valve and a check valve, on a communicating passage for communicating a compressing space in one of the compressing elements, and an inlet space of the other compressing element. SOLUTION: A compressing mechanism 61 of a compressor 5 comprises a pair of upper and lower cylinders 69, 70, a pair of upper and lower cylinder chambers 73, 75 formed by both sylinders 69, 70, and an intermediate plate 71, and a pair of upper and lower rotors 77, 79 eccentrically rotated along the inner peripheral faces of the both cylinder chambers 73, 75. A ratio of the discharge volumes of the rotors 77, 79 in the cylinder chambers 73, 75 is set, for example, 1:3. A power saving mechanism 81 is installed in such manner that it communicates the both cylinder chambers 73, 75. In the power saving mechanism 81, the check valves 98, 99 are mounted on the valve holes 87, 89 communicating the cylinder chamber 75 and a communicating hole 83, and the spool valves 92 are fitted to the valves 85, 87, 89 as the shut-off valves.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity compressor and an air conditioner equipped with the compressor, and to a technique for realizing multi-stage capacity control while reducing energy consumption.

[0002]

2. Description of the Related Art In recent air conditioners, in order to prevent overshooting and hunting at room temperature during cooling and heating,
The mainstream is to control the capacity on the heat source side (compressor) according to the capacity requirement of the user side (indoor heat exchanger).
As a method of controlling the capacity of a compressor, there are many methods of converting the frequency of an alternating current using an inverter device and thereby linearly controlling the driving speed of the compressor. According to this method, since the capacity of the compressor can be arbitrarily varied from 0 to the rated point, substantially perfect air conditioning control can be realized. However, the inverter device has various problems, such as inevitable energy loss due to frequency conversion, emission of undesired electromagnetic waves to the environment, and increase in device cost for large-sized devices.

In Japanese Patent Application Laid-Open No. Hei 8-247560, a variable-capacity type variable power control system in which a power saving mechanism and a refrigerant return circuit are used to control the capacity while using a constant speed compressor having a compression mechanism driven at a constant speed is used. Speed compressors have been proposed. The power save mechanism has a valve device attached to a cylinder side wall or the like of the compression mechanism. By opening the valve device, for example, the compression work in the first half of the compression stroke is not performed. Further, the refrigerant return circuit, for example, by providing a bypass circuit between the discharge side refrigerant circuit and the suction side refrigerant circuit of the compressor, and by opening a valve device interposed in the bypass circuit, the refrigerant after compression Is recirculated to the suction side refrigerant circuit.

When a variable-capacity constant-speed compressor is combined with a normal constant-speed compressor, the two compressors are individually operated or stopped, and a multi-stage is provided by using a power save mechanism and a refrigerant return circuit. Capability control becomes possible. For example, the rated capacity of the variable capacity constant speed compressor is 4 hp, the rated capacity of the constant speed compressor is 6 hp, the power reduction mechanism reduces the capacity of the variable capacity constant speed compressor by 2 hp, and the refrigerant return circuit. Assuming that the power reduction amount is one horsepower, the power is switched every one horsepower (that is, in ten steps) in the range of 1 to 10 horsepower.

[0005]

By the way, when the above-mentioned refrigerant return circuit is opened, a part of the compressed refrigerant flows back to the suction-side refrigerant circuit, so that the compressor performs useless compression work. . For example, when operating at a capacity of 9 hp, compression work of 1 hp is discarded by the refrigerant return circuit, but energy consumption is substantially the same as when operating at a capacity of 10 hp. As a result, energy loss equal to or greater than that of the inverter device occurs,
This was a factor that made it difficult to employ variable capacity constant speed compressors. Although consideration was given to performing the capacity control only by the power saving mechanism without providing the refrigerant return circuit, in that case, in the above-described compressor configuration, the capacity switching is performed every two horsepower (that is, five stages). Would. For this reason, in the air conditioner, when the capacity demand on the user side is small (for example, about 1 to 3 horsepower), overshooting or hunting at room temperature occurs, which may impair the user's comfort in the air-conditioned space. there were.

The present invention has been made in view of the above circumstances, and provides a compressor that achieves multi-stage capacity control while reducing energy consumption and the like, and an air conditioner equipped with the compressor. It is intended to be.

[0007]

Therefore, according to the present invention, the rotor comprises an eccentrically rotating rotor in a cylinder, and a vane slidingly contacting the outer peripheral surface of the rotor to define a suction space and a compression space. A multi-rotor compressor having a plurality of compression elements, wherein the plurality of compression elements have mutually exclusive volumes different from each other, and communicates a compression space of one compression element with a suction space of another compression element in a predetermined phase. And a power cut-off valve that is provided in the communication path and that includes a check valve that allows the fluid to pass only in one direction. suggest.

According to the present invention, when the shutoff valve of the power save means is closed, all the compression work is performed in each compression element, and the compressor is operated with the rated capacity. When the shut-off valve is opened, fluid flows out of the compression space of one compression element only into the suction space of the other compression element due to the action of the check valve provided in the communication passage, and the compressor saves power. It is operated in the state where it was done.

According to the second aspect of the present invention, there are provided a plurality of compression elements comprising a rotor which rotates eccentrically in a cylinder and a vane which slides on an outer peripheral surface of the rotor to define a suction space and a compression space. A compressor with a plurality of compression elements having different displacement volumes, wherein the compression stop means is provided in at least one of the compression elements and communicates a suction space of the compression element with the compression space. Propose what you have.

According to the present invention, when the compression stopping means does not operate, all compression work is performed in each compression element, and the compressor is operated with the rated capacity. Further, when the compression stop means provided in a certain compression element is operated, no compression work is performed in the compression element, and the compressor is operated in a state where the capacity corresponding to the displacement volume of the compression element is saved. .

According to the third aspect of the present invention, there are provided a plurality of compression elements comprising a rotor which rotates eccentrically in a cylinder and a vane which slides on an outer peripheral surface of the rotor to define a suction space and a compression space. A multi-rotor compressor in which the displacement volumes of the plurality of compression elements are different from each other, wherein the communication path communicates a compression space of one compression element with a suction space of another compression element at a predetermined phase; Power-save means comprising a shut-off valve for shutting off the flow of fluid in the communication passage, a check valve provided in the communication passage for allowing the fluid to pass only in one direction, and a power-saving means provided in at least one of the compression elements And a compression stop means for communicating the suction space of the compression element with the compression space.

According to the present invention, the compressor is operated with the rated capacity and also with the capacity saved in a plurality of stages, depending on the operating state of the power saving means and the operation of the compression stopping means.

Further, in the invention of claim 4, claims 1 to 3 are provided.
An air conditioner provided with the compressor according to any one of the above items is proposed.

According to the present invention, for example, a constant speed compressor having two compression elements is provided in the outdoor unit, and the constant speed compressor is provided with power saving means for moving the refrigerant between the two compression elements. A compression stopping means is provided for each compression element. Thereby, by performing drive control of both constant speed compressors and drive control of the power saving means and the compression stop means,
Multi-stage capacity control is realized without providing a refrigerant return circuit that causes energy loss.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a schematic configuration diagram of an air conditioner including one outdoor unit 1 and a plurality of indoor units 3. In FIG. 1, a refrigerant circuit is indicated by a solid line, and an electric circuit is indicated by a dashed line. is there.

On the outdoor unit 1 side, a compressor 5, an electromagnetic four-way valve 9, an outdoor heat exchanger 11, an electric fan 13, an accumulator 15, an oil separator 17, and the like are installed. Also, on the indoor unit 3 side, an electric expansion valve 21,
The indoor heat exchanger 23, the electric fan 25, etc. are installed. The devices that make up the refrigerant circuit are connected by refrigerant pipes 31 to 48 that are used to distribute gas refrigerant or liquid refrigerant. In the figure, reference numeral 27 denotes a normally closed solenoid on-off valve (hereinafter referred to as a first solenoid valve).
Reference numeral 29 denotes a three-position three-port type electromagnetic switching valve (hereinafter, referred to as a second solenoid valve), both of which are used to drive a power save mechanism described later.

The outdoor unit 1 includes an outdoor control unit (hereinafter referred to as an outdoor ECU) including a CPU, an input / output interface, a ROM, a RAM, and the like.
51) are provided. The outdoor ECU 51 includes:
Based on input information from a built-in control program and various sensors (not shown), the compressors 5 and 7, the four-way valve 9, the electric fan 13, and the first and second solenoid valves 27 and 29 are drive-controlled.

On the other hand, in the indoor unit 3, an indoor control unit (hereinafter referred to as an indoor E) comprising a CPU, an input / output interface, a ROM, a RAM, and the like.
CU) 52 are provided. Indoor ECU 52
Is based on input signals from a built-in control program and a remote controller (not shown) and various sensors.
The drive control of the electric expansion valve 21 and the electric fan 25 is performed, and signals are exchanged with the outdoor ECU 51.

In the case of this embodiment, the compressor 5 is an electric twin rotor type constant speed compressor having a pair of upper and lower rotary compression elements, and its rated output is set to 4 horsepower. The compressor 5 has a power save mechanism shown in FIG.
The compression work of the compressor 5 is switched to eight stages by their operation.

Hereinafter, the structure and operation of the power save mechanism according to the present embodiment will be described.

The compression mechanism 61 of the compressor 5 includes a pair of upper and lower cylinders 6 sandwiched between a main frame 65 and a bearing plate 67, as shown in a half vertical section in FIG.
9, 70, and a pair of upper and lower cylinder chambers 73, 75 defined by the cylinders 69, 70 and the intermediate plate 71.
18 along the inner peripheral surfaces of the two cylinder chambers 73 and 75.
A pair of upper and lower rotors 7 eccentrically rotating with a phase of 0 °
7,79.

In this embodiment, the two rotors 77 and 79 have the same diameter, but the ratio of the total height of the upper rotor 77 to the total height of the lower rotor 79 is set to 1: 3. Therefore, the ratio of the displacement volume of both rotors 77 and 79 in the upper cylinder chamber 73 and the lower cylinder chamber 75 is also 1: 3, and the upper rotary compression element has a rated output of 1 hp,
The lower rotating compression element will have a rated output of 3 hp. In the figure, reference numeral 80 denotes a compressor casing.

The power saving mechanism 81 is provided in both cylinder chambers 7.
3, 75 are communicated at predetermined communication portions (portions 180 ° out of phase with vanes described later).
9, 70 and a communication hole 83 formed in the outer peripheral portion of the intermediate plate 71 along the vertical direction, a first valve hole 85 communicating the upper cylinder chamber 73 with the communication hole 83, and a communication hole with the lower cylinder chamber 75. The second and third valve holes 87 and 89 communicating with the valve 83 are used as communication paths.

Each of the valve holes 85, 87 and 89 has a structure shown in FIG.
As shown in FIG. 2 (cross-sectional view taken along the line AA in FIG. 2), spool valve holes 91 are formed so as to intersect in the horizontal direction, and a spool valve 92 and a valve spring (compression coil) are formed in the spool valve holes 91. spring)
93 are stored. And the spool valve hole 9
A refrigerant gas introduction hole 94 is drilled at the right end of each of the spool valve holes 91 through the refrigerant gas introduction hole 94.
Refrigerant gas from the first to third power save pipes 44, 46, 47 is introduced therein.

In the present embodiment, the valve holes 85, 87, 89 are closed by the large-diameter portion 95 of the spool valve 92 when the low-pressure refrigerant gas is introduced from the refrigerant gas introduction hole 94. Then, a high pressure equal to or higher than a predetermined value (for example, the maximum discharge pressure of 10
%) Of the refrigerant gas is introduced, as shown in FIG.
The valve spring 93 is compressed to move the spool valve 92 to the left, and the valve holes 85, 87, 89 are opened via the small diameter portion 96 of the spool valve 92. In the figure, 97
Is a screw plug.

Reed valve type check valves 98 and 99 are provided in the second valve hole 87 and the third valve hole 89, respectively. The check valve 98 in the second valve hole 87 is a lower cylinder. The gas refrigerant flows only from the chamber 75 to the communication hole 83, and the check valve 99 in the third valve hole 89 allows the gas refrigerant to flow only from the communication hole 83 to the lower cylinder chamber 75.

The above-described first solenoid valve 27 is interposed between first and second bypass pipes 42 and 43 that connect the discharge side refrigerant pipe 31 and the suction side refrigerant pipe 41 of the compressor 5. The refrigerant gas introduction hole 94 on the first valve hole 85 side
Is connected to the first bypass pipe 42, and a capillary tube 49 for reducing the flow rate of the gas refrigerant is disposed upstream of the connection point.

On the other hand, the second solenoid valve 29 is a three-position three-port switching solenoid valve as described above. The first to third ports communicate with each other at the first position, and the first and third ports communicate with each other at the second position. The second port communicates with the first port and the third port at the third position. The first port of the second solenoid valve 29 is connected to a refrigerant pipe 45 branched from the first power save pipe 44, and the second port is connected to the second port.
A power save pipe 46 is connected, and a third power save pipe 47 is connected to the third port.

In the present embodiment, when the power save mechanism 81 is operated, the outdoor ECU 51 operates the first electromagnetic valve 27.
To close the first bypass pipe 45 and the second bypass pipe 4
6 is cut off. Then, the first bypass pipe 42
The high-pressure refrigerant gas from the discharge-side refrigerant pipe 31 is introduced into the spool valve hole 91 on the first valve hole 85 side via the first power save pipe 44, and the spool valve 92 is operated to activate the spool valve 92 as described above. One valve hole 85 is opened.

At the same time as the closing of the first solenoid valve 27, the outdoor side E
The CU 51 switches the second solenoid valve 29 to any one of the first to third positions. For example, when the second solenoid valve 29 is switched to the first position, the high-pressure refrigerant gas introduced into the first power save pipe 44 becomes the second and third power save pipes 4.
The second and third valve holes 87 and 89 are opened through the spool valve holes 91 on the side of the second and third valve holes 87 and 89 through the holes 6 and 47. In this state, the upper cylinder chamber 73 and the lower cylinder chamber 75 are connected to the respective valve holes 85 and 8.
The gas refrigerant flows out of the compression space of one cylinder chamber 73 (75) into the suction space of the other cylinder chamber 75 (73). Half of the compression work (ie, 50% = 2 horsepower for the compression mechanism 61 as a whole) is saved.

The outdoor ECU 51 is provided with the second solenoid valve 2.
When 9 is switched to the second position, the high-pressure refrigerant gas introduced into the first power save pipe 44 is introduced into the spool valve hole 91 on the second valve hole 87 side via the second power save pipe 46. , The second valve hole 87 is opened. In this state, the upper cylinder chamber 73 and the lower cylinder chamber 75 communicate with each other through the first and second valve holes 85 and 87 and the communication hole 83, and the check valve 98 operates to move the upper cylinder chamber 73 out of the compression space of the lower cylinder chamber 75. The gas refrigerant flows only into the suction space of the upper cylinder chamber 73, and half of the compression work in the lower cylinder chamber 75 (that is, 37.5% = 1.5 horsepower for the compression mechanism 61 as a whole) is saved.

Further, the outdoor ECU 51 is provided with the second solenoid valve 2.
When 9 is switched to the third position, the high-pressure refrigerant gas introduced into the first power save pipe 44 is introduced into the spool valve hole 91 on the third valve hole 89 side via the third power save pipe 47. , The third valve hole 87 is opened. In this state, the upper cylinder chamber 73 and the lower cylinder chamber 75 communicate with each other through the first and third valve holes 85 and 89 and the communication hole 83, and the check valve 99 acts to move the upper cylinder chamber 73 out of the compression space of the upper cylinder chamber 73. The gas refrigerant flows only into the suction space of the lower cylinder chamber 75, and half of the compression work in the upper cylinder chamber 73 (that is, 12.5% = 0.5 horsepower of the compression mechanism 61 as a whole) is saved.

On the other hand, when stopping the power saving mechanism 81, the outdoor ECU 51 opens the first solenoid valve 27 and switches the second solenoid valve 29 to the first position. Then, each spool valve hole 91 communicates with the suction-side refrigerant pipe 43 via the first to third power save pipes 44, 46, 47 and the second bypass pipe 43. Since the supply of the high-pressure refrigerant gas from the first bypass pipe 42 is extremely small due to the action of the capillary tube 49, the high-pressure gas refrigerant in each spool valve hole 91 flows out to the suction-side refrigerant pipe 43, and the spool valve 92 returns to the original position, and the first to third valve holes 85, 87, 89
Is closed.

As a result, all the compression work in both the cylinder chambers 73 and 75 is performed, and the compressor 5 generates a rated output (4 horsepower in this embodiment). The first and second bypass pipes 4 are provided in the capillary tube 49.
When they are communicated with each other via the refrigerant pipes 2 and 43, they also have an effect of minimizing the amount of high-pressure refrigerant gas flowing from the discharge-side refrigerant pipe 31 to the suction-side refrigerant pipe 41.

Next, the structure and operation of the compression stop mechanism according to this embodiment will be described.

As shown in FIG. 4, a compression stop mechanism 101 is provided in each of the cylinders 69 and 70 of the compressor 5, as shown in FIG.
Is incorporated. The compression stop mechanism 101 includes an electromagnetic stopper 103 embedded in each of the cylinders 69 and 70.
And a locking recess 107 formed in the vane 105. The electromagnetic stopper 103 has a built-in solenoid type actuator (not shown), and when activated, the lock pin 109 projects leftward in FIG.

During normal operation, as shown in FIG. 4, the lock pin 109 of the electromagnetic stopper 103 and the vane 1
05 is separated from the locking recess 107 of the vane 105.
Is pressed against the outer peripheral surface of the rotor 77 (rotor 79) by a vane spring (not shown). As a result, the upper cylinder chamber 73 (lower cylinder chamber 75) is
1 and the compression space 123, and the rotor 77 (rotor 7
Compression work is performed with the rotation of 9).

However, when the electromagnetic stopper 103 is driven (the solenoid is excited) by the drive current from the outdoor ECU 51, as shown in FIG.
Protrudes leftward in the figure, and its tip fits into the locking recess 107 of the vane 105. This prevents the vane 105 from projecting from the inner peripheral surface of the upper cylinder 69 (lower cylinder chamber 75), and the upper cylinder chamber 73 (lower cylinder chamber 7).
In 5), the suction and compression of the refrigerant are not performed at all.

Thus, in the compressor 5 of the present embodiment,
When the compression stop mechanism 101 on the upper cylinder 69 side operates, the compression work of 1 hp is saved, and when the compression stop mechanism 101 on the lower cylinder 70 side operates, the compression work of 3 hp is saved. When the electromagnetic stopper 103 is operated, the lock pin 109 instantaneously projects to the left.
The tip of the vane 105 is fitted into the locking concave portion 107 at the moment when the vane 105 is pushed into the upper cylinder 69 (lower cylinder 70) by the rotor 77.

Next, the flow of the refrigerant during the cooling operation will be described.

The gas refrigerant sucked from the accumulator 15 into the compressor 5 via the refrigerant pipe 41 is adiabatically compressed to be a high-temperature high-pressure gas refrigerant and discharged from the compressor 5. The discharged high-pressure gas refrigerant is supplied to the refrigerant pipe 3
1. After the course is controlled by the four-way valve 9 via the oil separator 17 and the refrigerant pipe 32, the refrigerant flows into the outdoor heat exchanger 11 via the refrigerant pipe 33. The high-temperature and high-pressure gas refrigerant is cooled by the outside air while passing through the inside of the outdoor heat exchanger 11 and condensed to become a liquid refrigerant. Then, the electric expansion of each indoor unit 3 via the refrigerant pipes 34 to 36. It flows into the valve 21.

After the flow rate of the liquid refrigerant is controlled by the electric expansion valve 21, the liquid refrigerant flows into the indoor heat exchanger 23,
While passing through the inside, it is vaporized to become a gas refrigerant, and cools the room air blown by the electric fan 25 by the latent heat of vaporization. At this time, the indoor-side ECU 52 controls the rotation speed of the electric fan 7 based on the deviation between the set temperature and the room temperature, and determines that the deviation between the inlet-side refrigerant temperature and the outlet-side refrigerant temperature of the indoor heat exchanger 23 is a predetermined value ( For example, the opening amount of the electric expansion valve 21 (the number of steps of the stepping motor for driving the valve body) is controlled so as to be 0 to 1 ° C.).

The gas refrigerant vaporized in the indoor heat exchanger 23 is
The refrigerant flows into the accumulator 15 via the refrigerant pipes 37 to 39, the four-way valve 9, and the refrigerant pipe 40, and is sucked into the compressor 5 again from the refrigerant pipe 41.

On the other hand, during the heating operation, the four-way valve 9 is switched as shown by the broken line, and the flow of the refrigerant is also opposite to that during the cooling operation, as shown by the arrow of the broken line. That is, the high-temperature high-pressure gas refrigerant discharged from the compressor 5 is introduced into the indoor heat exchanger 23, and then condensed into a liquid refrigerant while passing through the indoor heat exchanger 23, and the electric fan is condensed by latent heat of condensation. 2
5 heats the blown indoor air. Next, the liquid refrigerant flows into the outdoor heat exchanger 11, is heated by the outside air while passing through the inside of the outdoor heat exchanger 11, becomes a gas refrigerant by being vaporized, and then from the accumulator 15 to the compressor 5. It is inhaled again.

Hereinafter, the procedure of the capability control in this embodiment will be described with reference to the schematic diagrams of FIGS. In the schematic diagram, for convenience of explanation, the upper cylinder 69 and the lower cylinder 70 are vertically arranged, and the difference in volume is shown in a planarized manner. When the operation of the air conditioner is started, the outdoor ECU 51 determines the target compression work based on the input signal from each indoor ECU 52, and starts the compressor 5 (turns on the start magnet switch). ) Together with power saving control and compression stop control.

That is, as shown in FIG. 14, when the target compression work is 4 horsepower, the outdoor ECU 51 opens the first solenoid valve 27 and turns off the electromagnetic stopper 103. Then, the power save mechanism 81 and the compression stop mechanism 1
Since both the first and the second unit 01 do not operate, as shown in the schematic diagram of FIG. 6, a prescribed compression work is performed in both the cylinder chambers 73 and 75 of the compressor 5, and the outdoor unit 1 has a compression work of 4 hp. Done.

When the target compression work is 3.5 horsepower, the outdoor ECU 51 shuts off the first solenoid valve 27 and
The solenoid valve 29 is switched to the third position. Then, the gas refrigerant flows out of the compression space 123 of the upper cylinder chamber 73 into the suction space 121 of the lower cylinder chamber 75 as shown in the schematic diagram of FIG. Horsepower is saved. As a result, as a whole, the outdoor unit 1 reduces 0.5 hp from 4 hp and performs compression work of 3.5 hp.

When the target compression work is 3 horsepower, the outdoor EC
U51 opens the first electromagnetic valve 27 and drives the electromagnetic stopper 103 on the upper cylinder 69 side. Then
As shown in the schematic diagram of FIG. 8, the compression stop mechanism 101 stops the suction and compression of the refrigerant in the upper cylinder chamber 73 at all, and saves one horsepower as described above. As a result, as a whole, the outdoor unit 1 reduces 1 hp from 4 hp and performs compression work of 3 hp.

When the target compression work is 2.5 horsepower, the outdoor ECU 51 shuts off the first solenoid valve 27 and
The solenoid valve 29 is switched to the second position. Then, the gas refrigerant flows out of the compression space 123 of the lower cylinder chamber 75 into the suction space 121 of the upper cylinder chamber 73 by the power saving mechanism 81 as shown in the schematic diagram of FIG. Horsepower is saved. As a result, for the entire outdoor unit 1, 1.5 horsepower is reduced from 4 horsepower, and compression work of 2.5 horsepower is performed.

When the target compression work is 2 horsepower, the outdoor EC
U51 shuts off the first solenoid valve 27 and switches the second solenoid valve 29 to the first position. Then, as shown in the schematic diagram of FIG. 10, the power saving mechanism 81 moves the compression space 123 of the upper cylinder chamber 73 out of the lower cylinder chamber 7.
5 while the gas refrigerant flows out into the suction space 121 of the upper cylinder chamber 7 from the compression space 123 of the lower cylinder chamber 75.
The gas refrigerant flows out into the third suction space 121, and 2 horsepower is saved as described above. As a result, for the outdoor unit 1 as a whole, 2 hp is reduced from 4 hp, and compression work of 2 hp is performed.

When the target compression work is 1.5 horsepower, the outdoor ECU 51 closes the first solenoid valve 27 and sets the second solenoid valve 2
9 is switched to the second position, and the electromagnetic stopper 103 on the upper cylinder 69 side is driven. Then, as shown in the schematic diagram of FIG. 11, the compression space 12 of the lower cylinder chamber 75 is moved by the power saving mechanism 81 and the compression stopping mechanism 101.
Gas refrigerant flows out of the upper cylinder chamber 73 into the upper cylinder chamber 73, and no refrigerant is sucked and compressed in the upper cylinder chamber 73 at all, so that 2.5 horsepower is saved. As a result, as a whole, the outdoor unit 1 reduces compression power of 1.5 hp by reducing 2.5 hp from 4 hp.

When the target compression work is 1 hp, the outdoor EC
U51 opens the first electromagnetic valve 27 and drives the electromagnetic stopper 103 on the lower cylinder 70 side. Then
By the compression stop mechanism 101, as shown in the schematic diagram of FIG. 12, the suction and compression of the refrigerant are not performed at all in the lower cylinder chamber 75, and three horsepower is saved as described above. As a result, for the entire outdoor unit 1, 3 horsepower is reduced from 4 horsepower, and compression work of 1 horsepower is performed.

When the target compression work is 0.5 hp, the outdoor ECU 51 closes the first solenoid valve 27 and turns off the second solenoid valve 2.
9 is switched to the third position, and the electromagnetic stopper 103 on the lower cylinder 70 side is driven. Then, the power saving mechanism 81 and the compression stopping mechanism 101 cause the compression space 12 in the upper cylinder chamber 73 to move as shown in the schematic diagram of FIG.
The gas refrigerant flows out of the lower cylinder chamber 75 into the lower cylinder chamber 75, and no refrigerant is sucked and compressed in the lower cylinder chamber 75, thereby saving 3.5 horsepower. As a result, as a whole, the outdoor unit 1 reduces 3.5 hp from 4 hp and performs compression work of 0.5 hp.

As described above, in the present embodiment, as shown in FIG. 14, the power saving mechanism 81 and the compression stopping mechanism 10
By controlling the drive of No. 1, the capability control for every 0.5 hp from 0.5 to 4 hp could be realized. In this capacity control, energy efficiency could be improved by not performing the refrigerant return control for discarding the compression work.

The description of the specific embodiment has been completed.
Aspects of the present invention are not limited to this embodiment.
For example, in the above-described embodiment, a power save mechanism and a compression stop mechanism are provided in one constant speed compressor. However, a power save mechanism and a compression stop mechanism are provided in one of a plurality of constant speed compressors. It may be provided. In the above embodiment, the power save mechanism and the compression stop mechanism are provided in the twin rotor type constant speed compressor. However, the power save mechanism and the compression stop mechanism may be provided in the constant speed compressor having the triple rotor or more compression mechanism. . Further, as the power saving mechanism, for example, various structures such as providing a communication circuit and an electromagnetic valve outside the compressor casing are conceivable, and the amount of saving can be freely set. Further, a high-pressure refrigerant gas may be used as a drive source of the compression stop mechanism.
In addition, the specific configuration of the refrigerant circuit and the like can be appropriately changed without departing from the spirit of the present invention.

[0056]

As described above, according to the present invention,
A multi-rotor constant-speed compressor with different displacement volumes for each compression element is equipped with a power save mechanism and a compression stop mechanism, enabling multi-stage capacity control without performing refrigerant return control to discard compression work. Therefore, energy efficiency can be improved.

[Brief description of the drawings]

FIG. 1 is a refrigerant and electric circuit diagram showing an embodiment of an air conditioner according to the present invention.

FIG. 2 is a half vertical sectional view showing a structure of a power saving mechanism.

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

FIG. 4 is a half cross-sectional view showing a non-operation state of a compression stop mechanism.

FIG. 5 is a half transverse sectional view showing an operation state of a compression stop mechanism.

FIG. 6 is a schematic diagram showing the operation of the embodiment.

FIG. 7 is a schematic view showing the operation of the embodiment.

FIG. 8 is a schematic view showing the operation of the embodiment.

FIG. 9 is a schematic view illustrating the operation of the embodiment.

FIG. 10 is a schematic view showing the operation of the embodiment.

FIG. 11 is a schematic view showing the operation of the embodiment.

FIG. 12 is a schematic view illustrating the operation of the embodiment.

FIG. 13 is a schematic view illustrating the operation of the embodiment.

FIG. 14 is a diagram showing a relationship between a target compression work and the operation of each mechanism.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Outdoor unit 3 Indoor unit 5 Compressor 27 1st electromagnetic valve 29 2nd electromagnetic valve 51 Outdoor ECU 69 Upper cylinder 70 Lower cylinder 77, 79 Rotor 81 Power save mechanism 101 Compression stop mechanism 103 Electromagnetic stopper 105 Vane 121 Suction space 123 Compression space

Claims (4)

[Claims] 1. A compressor having a plurality of compression elements including a rotor that rotates eccentrically in a cylinder and a vane that slides on an outer peripheral surface of the rotor to define a suction space and a compression space. A multi-rotor compressor having different displacement volumes from each other, comprising: a communication path for communicating a compression space in one compression element with a suction space in another compression element in a predetermined phase; and a fluid passage in the communication path. A compressor provided with a power save means including a shut-off valve for shutting off a flow and a check valve provided in the communication passage and allowing the fluid to pass only in one direction. 2. A plurality of compression elements each comprising a rotor which rotates eccentrically in a cylinder, and a vane which slides on an outer peripheral surface of the rotor to define a suction space and a compression space. A multi-rotor compressor having a displacement volume different from each other, comprising compression stop means provided in at least one of the compression elements and communicating the suction space and the compression space of the compression element. Compressor. 3. A plurality of compression elements each comprising a rotor that rotates eccentrically in a cylinder and a vane that slides on an outer peripheral surface of the rotor to define a suction space and a compression space. A multi-rotor compressor having different displacement volumes from each other, comprising: a communication path for communicating a compression space in one compression element with a suction space in another compression element in a predetermined phase; and a fluid passage in the communication path. Power save means comprising a shutoff valve for shutting off a flow, a check valve provided in the communication path and allowing fluid to pass in only one direction, and a power save means provided in at least one of the compression elements, and suction of the compression element A compressor comprising: a compression stopping means for communicating a space with a compression space. 4. An air conditioner comprising the compressor according to claim 1.