CN112746961A

CN112746961A - Rotary compressor and refrigeration cycle device with same

Info

Publication number: CN112746961A
Application number: CN201911047909.1A
Authority: CN
Inventors: 小津政雄; 王玲; 高斌
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2019-10-30
Filing date: 2019-10-30
Publication date: 2021-05-04

Abstract

The invention discloses a rotary compressor and a refrigeration cycle device with the same. The rotary compressor includes: a housing in which a motor and a compression mechanism part driven by the motor are housed, the compression mechanism part including a cylinder having a compression chamber built therein, a crankshaft driven by the motor, a piston driven by the crankshaft and revolving in the compression chamber, and a slide plate reciprocating in the cylinder; the compression mechanism part is provided with a means for the compression chamber to enter a cylinder deactivation mode when the slide piece is stationary, and a means for the slide piece to abut against the piston and the compression chamber to enter a compression mode when the slide piece is stationary; and activation of the motor activates the compression mechanism portion in the cylinder deactivation mode. According to the rotary compressor of the present invention, the compression chamber can be switched between the cylinder deactivation mode and the compression mode, so that the restart time of the rotary compressor can be freely set.

Description

Rotary compressor and refrigeration cycle device with same

Technical Field

The invention relates to the field of compressors, in particular to a rotary compressor and a refrigeration cycle device with the same. The present invention relates to a technique for greatly shortening the restart time of a rotary compressor or freely setting the restart time.

Background

For example, a rotary compressor mounted in an air conditioner needs to be frequently stopped and restarted due to air conditioner temperature control, defrosting, and the like. In the prior art, no matter the variable frequency motor or the constant speed motor, after the compressor is stopped, the motor can not be accelerated until the shell pressure (high pressure) is the same as the suction pressure (low pressure), and the standby time is prolonged. As a result, a standby time of about 4 minutes is required before the rotary compressor is restarted (which is defined based on the conditions of use of the popular rotary compressor).

This standby time reduces the indoor comfort of the air conditioner, increases the energy loss of the air conditioner, and reduces APF (annual energy efficiency).

Disclosure of Invention

The present invention is directed to solving, at least to some extent, one of the above-mentioned problems in the prior art. Therefore, the invention provides a rotary compressor, which can freely set the restart time of the rotary compressor.

The invention also provides a refrigeration cycle device with the rotary compressor.

The rotary compressor according to an embodiment of the present invention includes: a housing in which a motor and a compression mechanism part driven by the motor are housed, the compression mechanism part including a cylinder having a compression chamber built therein, a crankshaft driven by the motor, a piston driven by the crankshaft and revolving in the compression chamber, and a slide plate reciprocating in the cylinder; the compression mechanism part is provided with a means for the compression chamber to enter a cylinder deactivation mode when the slide piece is stationary, and a means for the slide piece to abut against the piston and the compression chamber to enter a compression mode when the slide piece is stationary; and activation of the motor activates the compression mechanism portion in the cylinder deactivation mode.

According to the rotary compressor of the embodiment of the invention, the compression cavity can be switched between the cylinder deactivation mode and the compression mode, so that the restart time of the rotary compressor can be freely set.

According to some embodiments of the present invention, the compression mechanism portion includes a switch having a cylinder deactivation state where the vane is at rest and the compression chamber enters the cylinder deactivation mode, and a compression state where the vane is at rest released, the vane abuts the piston, and the compression chamber enters the compression mode.

According to some embodiments of the present invention, the compression mechanism portion is switched to the compression mode after being activated in the cylinder deactivation mode.

According to some embodiments of the invention, the compression mechanism portion stops moving due to the cylinder deactivation mode.

According to some embodiments of the invention, the switching member is a solenoid valve, which is a switching means between the cylinder deactivation mode and the compression mode.

According to some embodiments of the invention, in the cylinder deactivation mode, the solenoid is de-energized, the slide is stationary and separated from the piston; and under the compression mode, the electromagnetic valve is electrified, and the front end of the slide sheet is abutted against the periphery of the piston.

According to some embodiments of the present invention, the compression mechanism portion further includes a stopper, the slide plate has a stopper groove, when the solenoid valve is energized, the magnetic force generated by the solenoid valve attracts the stopper, an end of the stopper is disengaged from the stopper groove, and the compression chamber enters the compression mode; when the electromagnetic valve is powered off, the end part of the limiting stopper is embedded into the limiting groove, and the compression cavity enters the cylinder deactivation mode.

Optionally, the limiting groove is a conical groove, and the end of the limiter has a conical protrusion matched with the conical groove.

According to some embodiments of the invention, the stopper is in contact with a spring, and the spring is adapted to apply an elastic force to the stopper that moves the stopper toward the stopper groove.

According to another aspect of the present invention, a refrigeration cycle apparatus includes a condenser, an expansion device, an evaporator, and the above rotary compressor.

The refrigeration cycle device has the same advantages of the rotary compressor compared with the prior art, and the details are not repeated herein.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

FIG. 1 shows a cross-sectional view of a compressor with a solenoid valve in operation and a schematic of a refrigeration cycle (operating in compression mode) of an air conditioner coupled to the compressor;

fig. 2 shows a cross-sectional view of the internal structure of the compressor in operation (compression mode);

FIG. 3 is an external view of a slider with a conical slot;

FIG. 4 is a sectional view showing an internal structure of the compressor in operation switched from the "compression mode" to the "cylinder deactivation mode" of FIG. 2;

FIG. 5 is an X-sectional view of FIG. 4, a plan view of the cylinder and the interior of the compression pockets with the vane at rest (deactivated mode);

fig. 6 shows a plan view of the inside of the cylinder and compression chamber in operation after the compressor is restarted (compression mode);

fig. 7 shows a representative control stroke diagram of a compressor from a stop of operation to a restart and completion of the restart in operation.

Reference numerals:

the compressor comprises a 1A-rotary compressor, a 2-shell, a 4-motor, a 4 b-rotor, a 5A-compression mechanism part, a 6-air suction pipe, an 8-crankshaft, a 10-cylinder, a 11-compression cavity, a 12-sliding sheet groove, a 13-piston, a 15-sliding sheet, a 16-conical groove, a 20-electromagnetic valve, a 21-limiter, a 25-main bearing, a 30-auxiliary bearing and a 35-liquid storage device.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically connected, electrically connected or can communicate with each other; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

Fig. 1 shows a single-cylinder rotary compressor 1A and a refrigeration cycle of an air conditioner connected to the compressor 1A. The compressor 1A in operation is composed of a motor 4 fixed to the inner periphery of a hermetic casing 2, and a compression mechanism portion 5A driven by the motor 4, and lubricating oil is enclosed in the bottom of the casing 2 (not shown). The motor 4 is composed of a stator 4A fixed to the inner periphery of the casing 2 and a rotor 4b fixed to a crankshaft 8, and the crankshaft 8 is located at the center of the compression mechanism portion 5A.

The compression mechanism 5A includes a cylinder 10 having a compression chamber 11 therein, a main bearing 25 and a sub bearing 30 connecting upper and lower planes of the cylinder 10, a solenoid valve 20 fixed to the sub bearing 30, and a crankshaft 8 slidably fitted to the two bearings. These component parts are assembled by a plurality of screws, and the outer periphery of the cylinder 10 is fixed to the inner periphery of the housing 2.

The accumulator 35 is fixed to a side surface of the housing 2, and the suction pipe 6 having an opening to the accumulator 35 is connected to a side surface of the cylinder 10. Above the housing 2, which becomes high pressure during operation, there is an exhaust pipe 3 opening into the housing 2, and a power supply terminal 7 connected to the motor 4. The lower portion of the solenoid valve 20 is connected to the bottom surface of the housing 2.

An operation controller (not shown) located outside the compressor 1A switches the operation of the compression mechanism section 5A in operation to the "compression mode" and the "cylinder deactivation mode", respectively, by energizing and de-energizing the solenoid valve 20. The "compression mode" is a mode in which gas can be sucked and compressed in the compression chamber 11.

The "cylinder deactivation mode" is a mode in which the vane 15 (fig. 2) is stationary and thus the compression chamber 11 cannot suck and compress gas. These two modes of operation will be elucidated by means of figures 1-7 and the description below.

In fig. 1, the compressor 1A is stably operated in the "compression mode", and low-pressure gas sucked into the compression chamber 11 from the accumulator 35 through the suction pipe 6 is compressed into high-pressure gas, passes through the muffler chamber 26, and is discharged into the casing 2. Thereafter, the high-pressure gas is discharged from the gas discharge pipe 3 to the condenser 51 by the motor 4.

The high-pressure gas is condensed in the condenser 51, passes through the expansion valve 52, becomes a low pressure, and is evaporated in the evaporator 53. Thereafter, the low-pressure gas is sucked from the accumulator 35 into the compression chamber 11 through the suction pipe 6. The above is a refrigeration cycle, and a four-way valve is added to form a cycle for both refrigeration and heating.

In a household air conditioner using an R410A refrigerant or an R32 refrigerant, a discharge pressure (Pd, equivalent to a pressure of a casing 2) of a rotary compressor 1A during a steady operation is 2.5 to 3.0MpaG, a suction pressure (Ps, equivalent to a pressure of a suction pipe 6) is 0.8 to 1.0MpaG, and a steady pressure (Pd ═ Ps) after the compressor 1A is stopped is about 1.5 MpaG. After the compressor 1A stops, it takes 3 to 4 minutes to reach a stable pressure.

Fig. 2 is a sectional view of the compression mechanism portion 5A operating in the "compression mode". The compressor 1A in operation attracts the stopper 21 by a magnetic force generated when the solenoid valve 20 is energized, and the upper end of the stopper 21 is separated from the conical groove 16 located at the lower end of the vane 15. Therefore, the leading end of the vane 15 abuts against the outer periphery of the piston 13 and reciprocates. At this time, the spring 18 located at the rear end of the slide 15 expands and contracts.

The low-pressure gas sucked from the suction pipe 6 is compressed in the compression chamber 11, passes through the exhaust hole 25a and the exhaust valve 25b, and is discharged from the muffling chamber 26 to the internal space of the casing 2. As described above, the "compression mode" is operated in such a manner that the leading end of the reciprocating vane 15 abuts against the outer circumference of the piston 13, compresses and discharges the suction gas in the compression chamber 11.

Fig. 3 is an external view of the slider 15. The sliding piece 15 is rectangular and made of a material having excellent wear resistance. The lower surface 15d of the slide piece 15 has a conical groove 16 therein, and the conical groove 16 is a groove into which the tip of the stopper 21 of the solenoid valve 20 (i.e., the upper end of the stopper 21 in fig. 3 and 4) is fitted.

In the "compression mode", the stopper 21 is disengaged from the conical groove 16, and the slider 15 can freely reciprocate. On the other hand, in the "cylinder deactivation mode", the stopper 21 is fitted in the conical groove 16, and thus the vane 15 is stationary. The "compression mode" is switched by energizing the solenoid valve 20 and the "cylinder deactivation mode" is switched by de-energizing the solenoid valve 20.

Fig. 4 shows the compressor 1A operating in the "cylinder deactivation mode". In the "cylinder deactivation mode", the piston 13 revolves around the eccentric shaft 8a of the crankshaft 8, but the vane 15 is stationary and separated from the piston 13, and thus the suction and compression of the low-pressure gas in the compression chamber 11 are stopped.

In fig. 4, the motor 4 is stopped, and the compressor 1A is stopped in the "cylinder deactivation mode". Fig. 5 is the X-section of fig. 4 stationary in the "cylinder deactivation mode", showing the interior of the cylinder 10 and the stationary compression chamber 11. The stopper 21 is fitted into the conical groove 16 of the vane 15 which is stationary at the top dead center, and the vane 15 is stationary in the vane groove 12 of the cylinder 10.

Thereafter, if the motor 4 is energized, the stopped compressor 1A is restarted, and the crankshaft 8 to which the rotor 4b is fixed is rotated to revolve the piston 13. At this time, the "cylinder deactivation mode" means that the gas suction into the compression chamber 11, the compression load, and the sliding load of the crankshaft 8 are almost 0.

On the other hand, the rotation speed of the crankshaft 8 to which the high-mass rotor 4b is fixed is maximized after 4 to 6 seconds of energization of the motor 4, and the rotational force (rotational capacity) thereof is also maximized, and a balance weight is fixed to the rotor. During which the exhaust hole 25a is in a closed state.

Next, if the solenoid valve 20 is energized, the stopper 21 is disengaged from the conical groove 16 of the vane 15, and the vane tip 15a abuts against the outer periphery of the revolving piston 13, thereby switching to the "compression mode".

Fig. 6 is an internal plan view of the compression mechanism section 5A that operates after switching to the "compression mode". In the "compression mode" in which the crankshaft 8 rotates at a high speed, the suction and compression of gas and the discharge of gas from the discharge hole 25a are started in the compression chamber 11.

At this time, the pressure (high pressure) of the casing 2 maintaining the high pressure starts to rise, and the pressure (low pressure) of the intake pipe 6 starts to fall. That is, when the compressor 1A is started under an unbalanced pressure of the casing 2 > the pressure of the suction pipe 6, the compressor 1A quickly transitions to a steady operation state before the stop.

In this manner, if starting in the "cylinder deactivation mode", since the piston 13 and the crankshaft 8 rotate at full speed, the restart can be completed without being affected by the pressure condition before the compressor 1A stops. Therefore, the problem of long standby time of 4 minutes required for the restart in the past can be solved. In addition, the short-time restart can maintain the latent heat of the refrigeration cycle device to the maximum extent, and improve the APF and the comfort.

Further, when the compression mechanism 5A is switched from the "cylinder deactivation mode" to the "compression mode" during the start of the compressor 1A, the vane 15 abuts against the piston 13 that revolves at a high speed, but such abutment has been experienced in a two-cylinder capacity control rotary compressor for mass production, and it is possible to ensure that there is no problem with the reliability and noise of the vane.

For reference, if the compressor 1A is started in the "compression mode" under the condition that the pressure (Pd) > the pressure (Ps) of the intake pipe 6 in the casing 2, that is, the pressure difference Δ P (Pd — Ps) > 0, the exhaust valve 25b is closed by a force proportional to the pressure difference Δ P to close the exhaust hole 25a, and the compression pressure pulsating in the compression chamber 11 becomes the variable load torque of the rotating crankshaft 8 at the same time as the piston 13 is started.

However, since the motor start torque is not large enough with respect to the varying load torque, the compressor cannot be accelerated to cause a start failure. Therefore, in order to successfully start the rotary compressor in the "compression mode", it is necessary to start the rotary compressor with Δ P equal to 0 as in the conventional case.

Fig. 7 shows an example of a control routine from the stop of the operation to the restart of the compressor 1A that is started in the "cylinder deactivation mode".

First and second indicate a "cylinder deactivation mode" in which the vane 15 is stationary due to the stop of the solenoid valve 20 and then the motor 4, and the compressor 1A operating in the "compression mode" is stopped. And thirdly, starting the compressor 1A in the cylinder deactivation mode when the motor 4 is started, electrifying the electromagnetic valve 20 after the crankshaft 8 rotates for 4-6 seconds at full speed, releasing the slide sheet 15 from being static, and switching the compressor 1A to the compression mode for operation.

Further, the cylinder deactivation modes are provided between the first and fourth modes, and the second to third modes are the stop time of the compressor 1A. Further, the time of (i) to (ii) is for switching from the "compression mode" to the "cylinder deactivation mode", and therefore, there is no problem even in a short time of 5 seconds or less. The time from the third to the fourth is the acceleration time of the motor 4 and the crankshaft 8, and can be increased or decreased according to needs.

The standard control route of the compressor 1A from the stop of operation to the restart thereof is determined by a control command of the air conditioner. For example, the compressor 1A may be stopped for a short time of 1 minute or less, or may be stopped for 10 hours or more at night when no air conditioner is used. Further, when the compressor 1A is stopped, the energization of the motor 4 and the solenoid valve 20 is stopped, and therefore, no power consumption occurs.

For reference, since the single-cylinder compressor 1A has the functions of the "compression mode" and the "cylinder deactivation mode", the capacity can be controlled by the two modes in operation. The capacity control is based on the refrigeration capacity control of 100% and 0%.

In addition, in the double-cylinder rotary compressor, when the cold quantity control of the compressor 1A is applied to one cylinder, the capacity control of 100 percent, 50 percent and the like can be realized as the same as the volume production. Therefore, the starting and the cold quantity control of the compressor are easy to be carried out by applying the invention to the double-cylinder rotary compressor.

The rotary compressor according to the embodiment of the invention has the following beneficial effects:

(1) the rotary compressor is restarted regardless of the casing pressure and the suction pressure before stopping. I.e. it can be restarted if necessary.

(2) When the rotary compressor is restarted, high pressure and low pressure are continued, the latent heat energy loss of the refrigeration cycle device is less, and the time required for the rotary compressor to reach stable operation is short.

(3) The comfort of the air conditioner can be improved, and the annual energy efficiency (APF) can be improved.

(4) The above effects can be applied to constant speed motors and variable speed variable frequency motors.

(5) The technique of the compressor 1A can be applied to one or both cylinders of a two-cylinder rotary compressor.

(6) The present invention can be easily implemented by modifying a conventional rotary compressor.

The rotary compressor 1A according to an embodiment of the present invention will be described in detail with reference to fig. 1 to 7.

Referring to fig. 1-2 and 4, a rotary compressor 1A according to an embodiment of the present invention may include a housing 2, a motor 4 and a compression mechanism 5A are housed in the housing 2, the compression mechanism 5A is driven by the motor 4, the compression mechanism 5A includes a cylinder 10, a crankshaft 8, a piston 13 and a vane 15, wherein a compression cavity 11 is built in the cylinder 10, the crankshaft 8 is driven by the motor 4, the piston 13 is driven by the crankshaft 8 and revolves in the compression cavity 11, a vane slot 12 is opened on the cylinder 10, and the vane 15 reciprocates in the vane slot 12.

The compression mechanism part 5A has a means for bringing the compression chamber 11 into a cylinder deactivation mode when the vane 15 is stationary, and a means for bringing the vane 15 into contact with the piston 13 and bringing the compression chamber 11 into a compression mode when the vane 15 is released from being stationary; and activation of the motor 4 causes the compression mechanism portion 5A to be activated in the cylinder deactivation mode.

According to the rotary compressor 1A of the embodiment of the present invention, the compression chamber 11 can be switched between the cylinder deactivation mode and the compression mode, so that the restart time of the rotary compressor 1A can be freely set.

The compression mechanism 5A has a switching member for switching the compression chamber 11 to the cylinder deactivation mode when the vane 15 is stationary, and a switching member for switching the compression chamber 11 to the compression mode when the vane 15 is stationary and released and the vane 15 abuts on the piston 13.

The compression mechanism section 5A includes a switching member having a cylinder deactivation state in which the vane 15 is stationary, the vane 15 is separated from the piston 13, and the compression chamber 11 enters the cylinder deactivation mode, and a compression state in which the vane 15 is stationary released, the vane 15 abuts against the piston 13, and the compression chamber 11 enters the compression mode.

After the compression mechanism unit 5A is started in the cylinder deactivation mode, it is switched to the compression mode.

The compression mechanism portion 5A stops moving due to the cylinder deactivation mode.

Specifically referring to fig. 7, in the cylinder deactivation mode, the switching member is in the cylinder deactivation state, the sliding vane 15 is stationary, when the motor 4 is stopped, the compression mechanism 5A is stopped, and the compression process of the compressor is stopped, which corresponds to the second stage in fig. 7, and when the motor 4 is started, the compression mechanism 5A is started, and the crankshaft 8 rotates to make the piston 13 revolve, which corresponds to the third stage in fig. 7.

The numbers from (ii) to (iii) in fig. 7 indicate the stop time of the compressor 1A.

The rotating speed of the crankshaft 8 reaches the maximum after the motor 4 is electrified for 4-6 seconds, the switching piece correspondingly moves at the moment and enters a compression state, the section corresponds to the section IV in the figure 7, so that the sliding sheet 15 is stopped and removed, the front end 15a of the sliding sheet is abutted against the periphery of the revolving piston 13, the compression cavity 11 enters a compression mode, and the compression process of the compressor is restarted accordingly.

The time from the third to fourth in fig. 7 is the acceleration time of the motor 4 and the crankshaft 8, and can be increased or decreased as needed.

In the normal compression process of the compressor, if the switching piece is placed in the cylinder deactivation state again, the motor 4 is still in the power-on state, but the sliding piece 15 is still stationary and separated from the piston 13, so that at this time, although the crankshaft 8 rotates to make the piston 13 revolve, the suction and compression of the low-pressure gas in the compression cavity 11 are stopped, and the section corresponds to (i) to (ii) in fig. 7.

Only in the cylinder deactivation mode, the compression mechanism portion 5A is stopped, and after the compression mechanism portion 5A is activated, the compression chambers 11 can be switched to the compression mode when the switching member is switched to the compression state.

The time points of the first, second, third and fourth can be controlled manually, so the restart time of the rotary compressor can be set freely, for example, the restart time of the rotary compressor can be shortened.

The switching member is an electromagnetic valve 20. By controlling the energization or deenergization of the solenoid valve 20, the switching member can be controlled to be in the compression state or the cylinder deactivation state.

Further, the solenoid valve 20 is a switching means between the cylinder deactivation mode and the compression mode.

In the cylinder deactivation mode, the electromagnetic valve 20 is powered off, and the sliding sheet 15 is static and separated from the piston 13; in the compression mode, the solenoid valve 20 is energized, and the tip of the slide piece 15 abuts against the outer periphery of the piston 13.

The compression mechanism part 5A further includes a stopper 21, the slide piece 15 has a stopper groove, as shown in fig. 1-2, 4 and 6, when the electromagnetic valve 20 is energized, the magnetic force generated by the electromagnetic valve 20 attracts the stopper 21, the end of the stopper 21 is disengaged from the stopper groove, and the compression chamber 11 enters the compression mode; referring to fig. 1 to 2 and 4 to 5, when the solenoid valve 20 is de-energized, the end of the stopper 21 is inserted into the stopper groove, and the compression chamber 11 enters the cylinder deactivation mode.

Optionally, the limiting groove is a conical groove 16, the end of the limiter 21 is provided with a conical protrusion matched with the conical groove 16, and the conical structure can play a good guiding role, so that the end of the limiter 21 can be conveniently embedded into the conical groove 16.

The stopper 21 is in contact with a spring adapted to apply an elastic force to the stopper 21 to move the stopper 21 toward the stopper groove.

Referring to fig. 1 to 2 and 4 to 5, the solenoid valve 20 is disposed at the bottom of the cylinder 10, and the stopper groove is disposed at the lower surface of the sliding piece 15. In some embodiments, the spring is a compression spring located below the stopper 21 for applying a pushing force to the stopper 21 to move the stopper 21 toward the stopper groove. In other embodiments, the spring is an extension spring, which is located above the stopper 21 and is used to apply a pulling force to the stopper 21 to move the stopper 21 toward the stopper groove.

A refrigeration cycle apparatus according to another aspect of the embodiment of the present invention includes a condenser, an expansion device, an evaporator, and the rotary compressor 1A of the above-described embodiment.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example" or "some examples" or the like are intended to mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples described in this specification can be combined and combined by those skilled in the art.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A rotary compressor, comprising:

a housing in which a motor and a compression mechanism part driven by the motor are housed, the compression mechanism part including a cylinder having a compression chamber built therein, a crankshaft driven by the motor, a piston driven by the crankshaft and revolving in the compression chamber, and a slide plate reciprocating in the cylinder;

the compression mechanism part is provided with a means for the compression chamber to enter a cylinder deactivation mode when the slide piece is stationary, and a means for the slide piece to abut against the piston and the compression chamber to enter a compression mode when the slide piece is stationary;

and activation of the motor activates the compression mechanism portion in the cylinder deactivation mode.

2. The rotary compressor of claim 1, wherein the compression mechanism part comprises a switch having a cylinder deactivation state in which the vane is at rest and the compression chamber enters the cylinder deactivation mode, and a compression state in which the vane is at rest released, the vane abuts the piston, and the compression chamber enters the compression mode.

3. The rotary compressor of claim 1 or 2, wherein the compression mechanism part is switched to the compression mode after being activated in the cylinder deactivation mode.

4. The rotary compressor of claim 1 or 2, wherein the compression mechanism portion stops moving due to the cylinder deactivation mode.

5. The rotary compressor of claim 2, wherein the switching member is a solenoid valve, which is a switching means between the cylinder deactivation mode and the compression mode.

6. The rotary compressor of claim 5, wherein in the cylinder deactivation mode, the solenoid valve is de-energized, the vane is stationary and separated from the piston; and under the compression mode, the electromagnetic valve is electrified, and the front end of the slide sheet is abutted against the periphery of the piston.

7. The rotary compressor of claim 5, wherein the compression mechanism part further comprises a stopper, the vane has a stopper groove, when the solenoid valve is energized, a magnetic force generated by the solenoid valve attracts the stopper, an end of the stopper is separated from the stopper groove, and the compression chamber enters the compression mode; when the electromagnetic valve is powered off, the end part of the limiting stopper is embedded into the limiting groove, and the compression cavity enters the cylinder deactivation mode.

8. The rotary compressor of claim 7, wherein the limiting groove is a conical groove, and the end of the limiting stopper has a conical protrusion engaged with the conical groove.

9. The rotary compressor of claim 7, wherein the stopper is in contact with a spring, and the spring is adapted to apply an elastic force to the stopper to move the stopper toward the stopper groove.

10. A refrigerating cycle apparatus comprising a condenser, an expansion device, an evaporator and the rotary compressor of any one of claims 1 to 9.