CN112412790B

CN112412790B - Rotary compressor and refrigeration cycle device

Info

Publication number: CN112412790B
Application number: CN201910785885.3A
Authority: CN
Inventors: 小津政雄; 高斌; 王玲
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2019-08-23
Filing date: 2019-08-23
Publication date: 2022-03-01
Anticipated expiration: 2039-08-23
Also published as: CN112412790A

Abstract

The invention discloses a rotary compressor and a refrigeration cycle device. The rotary compressor comprises a closed shell, a motor, a compression mechanism part driven by the motor, an exhaust pipe for opening a hole in the shell, an air suction pipe connected with the compression mechanism part, a pressure equalizing device for communicating the interior of the shell with the air suction pipe, and a liquid storage device connected with the air suction pipe outside the shell and a first check valve device, wherein when the motor stops, a bypass hole of the pressure equalizing device is opened, the first check valve device is closed, and gas in the shell flows into the air suction pipe or the liquid storage device. According to the rotary compressor provided by the invention, the restarting time of the rotary compressor can be greatly shortened, the APF can be further improved, the pressure equalizing device and the first check valve device are automatically controlled by utilizing pressure difference, the cost is low, the reliability is high, electric control is not needed, and the energy is saved.

Description

Rotary compressor and refrigeration cycle device

Technical Field

The invention relates to the field of compressors, in particular to a rotary compressor and a refrigeration cycle device. The present invention relates to a technique for greatly reducing the restart time of a rotary compressor for converting the internal pressure of a sealed casing into a high pressure. The capacity control and energy efficiency per year (APF) of air conditioners and freezers can be improved using this technique.

Background

Under the conditions of air-conditioning room temperature control, defrosting operation and the like, the compressor can frequently and repeatedly start and stop. However, the rotary compressor in which the internal pressure of the hermetic shell is high has problems that: if the shell pressure or discharge pressure is not equal to the suction pressure of the compression chamber, the motor cannot start.

Therefore, it takes about 4 minutes to restart after the compressor is stopped, and it takes time for the casing pressure of the restarted compressor to change from a low pressure to a high pressure. As a result, there are disadvantages such as deterioration of the control of the air conditioner room temperature and an increase in the defrosting operation time required for the heating operation, and these problems also cause an influence on the annual energy efficiency (APF).

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 present invention provides a rotary compressor to shorten 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 motor and a compression mechanism part driven by the motor are arranged in the closed shell; an exhaust pipe communicating with an interior of the housing; the air suction pipe is connected with the compression cavity of the compression mechanism part; the pressure equalizing device is provided with a bypass hole for communicating the inside of the shell with the air suction pipe; the device comprises a liquid storage device, one end of the liquid storage device is connected with the air suction pipe, the other end of the liquid storage device is connected with a first check valve device, when the motor stops, a bypass hole of the pressure equalizing device is opened, the first check valve device is closed, and gas in the shell flows into the air suction pipe or the liquid storage device.

According to some embodiments of the invention, the first check valve device is a one-way valve or a solenoid switch valve.

According to some embodiments of the present invention, the compression mechanism portion is activated using the motor according to a pressure difference between the housing and the reservoir.

According to some embodiments of the invention, the exhaust pipe has a second check valve arrangement, the second check valve arrangement closing when the pressure in the housing decreases.

According to some embodiments of the invention, the second check valve device is a one-way valve or a solenoid switch valve.

According to some embodiments of the present invention, the pressure equalizing device of the rotary compressor comprises: a bypass valve opening or closing the bypass hole, and a spring expanding and contracting by a pressure difference between the case pressure and the reservoir.

According to some embodiments of the present invention, a high pressure side opening end of the bypass hole is located in a muffler of the compression mechanism part.

According to some embodiments of the present invention, the compression chamber of the compression mechanism includes at least a revolving rolling piston and a sliding piece that abuts against an outer periphery of the rolling piston and reciprocates.

According to some embodiments of the invention, the compression mechanism portion comprises: the air suction pipe comprises an air cylinder, a main bearing and an auxiliary bearing, wherein the main bearing is located at one end of the air cylinder, the auxiliary bearing is located at the other end of the air cylinder, a compression cavity is formed in the air cylinder, and the air suction pipe is communicated with the compression cavity.

According to some embodiments of the invention, the muffler has a muffler exhaust opening communicating with the interior of the housing.

According to some embodiments of the present invention, the bypass valve selectively communicates the bypass hole with the suction pipe using a pressure difference between the casing pressure and the accumulator, and the spring moves the bypass valve in a direction to open the bypass hole.

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

1) the restart time of the rotary compressor can be greatly shortened, and the APF (annual energy efficiency) can be improved.

2) The pressure equalizing device and the first check valve device are automatically controlled by pressure difference, so that the pressure equalizing device is low in cost, high in reliability, free of electric control and beneficial to energy conservation.

According to another aspect of the present invention, a refrigeration cycle apparatus includes the rotary compressor.

The refrigeration cycle apparatus has the same advantages as the above-mentioned rotary compressor over the prior art, and is not described herein again.

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 is a schematic view of an air conditioning refrigeration cycle in steady operation incorporating the compressor of the present invention;

FIG. 2 is a schematic view of the internal construction of the compressor in operation;

FIG. 3 is a schematic view of section X-X of FIG. 2;

FIG. 4 is a schematic sectional view of a compression mechanism portion showing the configuration of a pressure equalizer;

FIG. 5 is a schematic view showing the internal structure of the compressor after the compressor is stopped;

fig. 6 is a pressure distribution diagram of the refrigeration cycle apparatus when the pressures of the casing, the accumulator, the compression chamber, and the like become equal after the compressor is stopped;

fig. 7 is a schematic diagram showing the change of the exhaust of the casing and the change of the pressure inside the accumulator after the compressor in the steady operation starts to stop and the restart is completed.

Reference numerals:

1-compressor, 2-shell, 3-exhaust pipe, 5-compression mechanism part, 6-motor, 8-lubricating oil, 10-cylinder, 11-compression cavity, 12-suction hole, 13-suction pipe, 14-sliding sheet groove, 15-rolling piston, 16-sliding sheet, 20-main bearing, 21-main shaft plate, 23-muffler, 24-exhaust valve, 21 a-exhaust hole, 25-auxiliary bearing, 30-pressure equalizing device, 32-bypass valve, 33-bypass hole, 34-coil spring, 35-limiter, 40-crankshaft, 45-reservoir, 47-low pressure pipe, 48-central pipe, 50-condenser, 51-electric expansion valve, 52-evaporator, 53-first check valve device, etc, 54-second check valve means.

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 "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but 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, are not to be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

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.

A rotary compressor according to an embodiment of the present invention will be described in detail with reference to fig. 1 to 7. In order to improve the above problems, the rotary compressor of the present invention is characterized in that the pressure of the hermetic shell is maintained at a middle pressure, and the compressor is stopped and restarted. The details are shown in the following examples. Typical examples of the rotary compressor include a rotary compressor and a scroll compressor in which the internal pressure of the casing is high.

Fig. 1 shows a schematic diagram of an air-conditioning refrigeration cycle during a steady operation of a compressor 1 including the present invention. The low-pressure refrigerant in the accumulator 45 is sucked from the suction pipe 13 of the compressor 1 into the compression chamber 11, and the high-pressure gas compressed in the compression chamber 11 is discharged to the hermetic shell 2.

The high-pressure refrigerant discharged from the exhaust pipe 3 moves to the condenser 50 through the second check valve device 54, and the condensed liquid refrigerant passes through the motor-operated expansion valve 51 to become a low-pressure refrigerant, is evaporated in the evaporator 52 to become a low-pressure gas, and flows into the accumulator 45 from the low-pressure pipe 47 through the first check valve device 53.

The compressor 1 is characterized in that a pressure equalizer 30 is provided in a compression mechanism 5 fixed inside the casing 2, and as described later, when the compressor 1 is in operation, a bypass hole 33 of the pressure equalizer 30 is closed, and high-pressure gas in the casing 2 does not flow into the suction pipe 13.

Fig. 2 shows the internal structure of the compressor 1 during operation. Fig. 3 shows a cross-section X-X in fig. 2. In fig. 2, the motor 6 and the compression mechanism 5 are incorporated in the casing 2, and the lubricant oil 8 is incorporated in the bottom of the casing 2. The outer periphery of the cylinder 10 of the compression mechanism 5 is fixed to the inner periphery of the casing 2 by spot welding, and the main bearing 20 and the sub bearing 25 seal the cylindrical compression chamber 11 at the center of the cylinder 10.

The crankshaft 40 driven by the motor 6 is slidably engaged with the main bearing 20 and the sub bearing 25, and the crankshaft 40 drives the rolling piston 15 to revolve in the compression chamber 11. At this time, the rolling piston 15 sucks in low-pressure gas and discharges the gas from the exhaust hole 21a of the exhaust valve 24 to the muffler 23. After that, the high-pressure gas is discharged from the gas discharge pipe 3 through the motor 6.

The cylindrical reservoir 45 fixed outside the housing 2 is connected to a low pressure pipe 47 at the upper part thereof and has a center pipe 48 at the center thereof, as in the case of the general reservoir. The intake pipe 13 is connected to a bent pipe at the lower end of the center pipe, and the intake pipe 13 is press-fitted into an intake hole 12 that opens into the compression chamber 11 from the outer periphery of the cylinder 10. A small amount of liquid refrigerant is stored in the reservoir 45.

The compressor 1 is provided with a pressure equalizer 30 on a main shaft plate 21 of a main bearing 20, the pressure equalizer 30 is provided with a bypass hole 33, and an upper opening end of the bypass hole 33 is positioned inside a muffler 23. As shown in fig. 3, the tip of a vane 16 reciprocating in a vane groove 14 of the cylinder 10 abuts on the outer periphery of a rolling piston 15 revolving in the compression chamber 11. The pressure equalizing device 30 is disposed above the suction hole 12.

Fig. 4 is a cross section of the compression mechanism section 5, and shows the structure of the pressure equalizer 30. The pressure equalizer 30 has a bypass hole 33 at the center of a cylindrical hole 31 formed in the main shaft plate 21, and the lower end of the bypass hole 33 communicates with the intake hole 12 of the cylinder 10. During operation of the compressor 1, the bypass valve 32 is stationary at the upper end of the bypass hole 33, and the bypass valve 32 is an on-off valve.

The coil spring 34 and the stopper 35 are provided at the bottom and the upper portion of the cylindrical hole 31, respectively, and the coil spring 34 presses the bypass valve 32 toward the stopper 35. In the operation of the compressor 1, the pressure inside the casing 2 becomes high, and the suction port 12 becomes low, so that the bypass valve 32 closes the bypass port 33.

However, when the pressure of the casing 2 is reduced and the pressure of the intake port 12 is increased after the compressor 1 is stopped, the bypass hole 33 is opened by the pressing force of the coil spring 34, and the outer periphery of the bypass valve 32 is stopped at the stopper 35. Therefore, as shown in the upper right of fig. 4, the high-pressure gas in the housing 2 flows out to the suction hole 12 through the bypass hole 33.

When the compressor 1 is stopped, the pressure in the casing 2 decreases and the pressure in the suction port 12 increases, which is a phenomenon that the pressure in the casing 2 having the compression mechanism 5 built therein becomes high. For example, the compressor 1 is a rotary compressor, and as shown in fig. 3, the inner diameter of a rolling piston 15 that orbitally slides and a back hole 14a of a vane 16 that reciprocally slides are high pressure, and high pressure gas in the casing 2 leaks into the compression chamber 11 through a sliding gap between the sliding surfaces of the components. That is, in the operation of the compressor 1, all the gas leaked into the compression chamber 11 is compressed again and discharged into the casing 2.

However, as shown in fig. 5, after the compressor 1 is stopped, the discharge hole 21a is closed by the discharge valve 24, and the gas leaked to the compression chamber 11 flows to the accumulator 45 through the suction pipe 13. Therefore, the pressure of the casing 2 decreases, and the pressure of the reservoir 45 increases. In addition, the evaporator 52 maintains a low pressure because the first check valve device 53 prevents the high pressure gas flowing to the accumulator 45 from flowing to the evaporator 52.

When the pressure of the casing 2 becomes low, the pressure of the casing 2 becomes lower than the pressure of the condenser 50. At this time, the second check valve device 54 is closed. Therefore, the condenser 50 can maintain a high pressure state before the operation is stopped. At this time, the motor-operated expansion valve 51 is closed by control. However, since the capillary valve or the like cannot perform valve control, the condenser 50 pressure slowly drops and the evaporator 52 pressure increases.

Fig. 6 shows the pressure distribution of the refrigeration cycle apparatus when the pressures of the casing 2, the accumulator 45, the compression chamber 11, and the like become equal after the compressor 1 is stopped. The pressure in the accumulator 45 corresponds to the pressure in the shell 2, and the pressure in the shell 2 is high and lower than the pressure in the condenser 50.

Here, an example is: in a rotary compressor mounted in a household air conditioner, the total volume of a compression mechanism part 5, a motor 6 and a lubricating oil 8 is removed, the space volume (C) of a housing 2 is about 2100cc, and the internal volume (A) of an accumulator 45 is about 700cc, so that the accumulator volume is 1/3 of the housing space volume.

On the other hand, when the refrigerant used in the air conditioner is R410A, the internal pressure of the casing 2 before the operation is stopped is 3.0MPaA, and the internal pressure of the accumulator 45 is 1.0MPaA, the compressor 1 stops the flow of the high-pressure gas from the casing 2 to the accumulator 45, and as a result, the both become equal to 2.5MPaA at night.

As a result, the pressure of the shell 2 of the compressor 1 in operation decreases from 3.0mpa to 2.5mpa, and the pressure of the accumulator 45 increases from 1.0mpa to 2.5 mpa. After the compressor 1 stops operating and the pressure of the accumulator 45 is equal to the pressure of the shell 2 of the compressor 1, the compressor 1 can be restarted and the pressure rise speed is increased significantly.

Next, the motor 6 is energized from the stationary state shown in fig. 6, and after the compressor 1 is restarted, the rolling piston 15 revolves to cause the high-pressure gas in the accumulator 45 to flow into the compression chamber 11. At this time, the pressure of the reservoir 45 is equal to the gas pressure of the casing 2, and the motor can be restarted without causing a large load.

After the start, for example, since the bypass hole 33 of the pressure equalizing device 30 is opened within 10 seconds, the pressure difference between the casing 2 and the accumulator 45 does not rapidly increase, and the high-pressure gas of the compression chamber 11 is compressed and then passes through the discharge hole 21 a. And then mixed into the high-pressure gas in the casing 2.

When the pressure difference between the casing 2 and the accumulator 45 exceeds a predetermined design value after the operation of the compressor 1, the bypass hole 33 is closed, the pressure rise of the casing 2 is accelerated, and the pressure drop of the accumulator 45 is accelerated.

At this time, the pressure of the casing 2 rises, the pressure of the carrier of the second check valve device 54 drops due to the pressure of the reservoir 45, and the first check valve device 53 opens. At the same time, the opening degree of the motor-operated expansion valve 51 is optimized in accordance with the temperatures of the evaporator 52 and the condenser 50, and the refrigeration cycle apparatus transitions to a stable operation.

Assuming that the refrigeration cycle apparatus of fig. 7 is the above-described household air conditioner, the change in the discharge air of the casing 2 is shown by a solid line (a1) after the compressor 1 in the steady operation starts to stop until the restart is completed, and the change in the internal pressure of the accumulator 45 is shown by a solid line (a 2). In comparison with the compressor 1, the shell pressure change of the conventional compressor is shown by a broken line (B1), and the accumulator pressure change is shown by a broken line (B2).

The horizontal axis is process time, expressed in minutes (min) by numbers; the vertical axis represents pressure (MPaA). The time from the start of the compressor to the restart was set to 10 seconds, and it was confirmed whether the two pressures were equal to each other.

Arrow ↓ indicates a time when the high-pressure side pressure and the low-pressure side pressure after the compressor is stopped become equal, and arrow ≠ indicates a time when the restart is completed after the compressor is restarted and the pressure is equal to the pressure before the operation stop.

After the operation of the compressor 1 is stopped, the high pressure (a1) and the low pressure (a2) are gradually lowered or raised, respectively, and as indicated by arrows ≠ 20, the bypass hole 33 is opened after about 20 seconds, the high pressure (a1) and the low pressure (a2) are rapidly lowered or raised, respectively, and the pressures become equal after about 50 seconds of the operation stop. The pressure was 2.5 MPaA. After that, the compressor was restarted after another 10 seconds, and the pressure was the same as the pressure before the compressor 1 was stopped 1 minute and 50 seconds after the operation was stopped.

In the conventional compressor, after the operation is stopped, the high pressure (B1) and the low pressure (B2) are gradually lowered and raised, respectively. But then the decrease and increase in air pressure become slow, equivalent after about 2 minutes and 40 seconds. The pressure was about 1.9 MPaA. The compressor was restarted after 10 seconds, and the pressure before the operation was stopped was equivalent to about 4 minutes and 30 seconds after the operation was stopped. As a result, the time from the stop of the operation of the compressor 1 to the completion of the restart thereof was 40% of that of the conventional compressor.

The reason for the time difference is two:

(1) after the compressor 1 stops operating, the pressure is exchanged between the casing 2 and the accumulator 45, and the pressure is accelerated for the same time. Further, since the equilibrium pressure is high and 2.5MPaA, the time required for returning to the pressure before the start/stop is short.

(2) In the conventional compressor operation, a compressor housing and a condenser are high-pressure vessels, an evaporator and a reservoir are low-pressure vessels, and after the compressor is stopped, a high-pressure refrigerant (a refrigerant containing liquid) in the high-pressure vessel flows out to the evaporator through an expansion valve (or a capillary tube), so that the vessels are equalized in pressure. Therefore, it takes a long time to achieve voltage equalization. Further, the equilibrium force was a medium pressure of 1.9MPaA, and the time required for returning to the pre-start-stop pressure was long. The above is the time difference of the start of the compressor.

Referring to fig. 1 to 2 and 5 to 6, a rotary compressor 1 according to an embodiment of the present invention may include: the casing 2, motor 6, compressing mechanism portion 5, blast pipe 3, breathing pipe 13, pressure equalizing device 30, reservoir 45, casing 2 can be sealed housing, motor 6 sets up in casing 2, compressing mechanism portion 5 sets up in casing 2 and is driven by motor 6, blast pipe 3 communicates with the inside of casing 2, breathing pipe 13 is connected with compressing mechanism portion 5, pressure equalizing device 30 has the by-pass opening 33 that communicates the inside of casing 2 with breathing pipe 13, in order to communicate the inside of casing 2 with breathing pipe 13 selectively, the one end of reservoir 45 is connected with breathing pipe 13, the other end of reservoir 45 is provided with first check valve device 53.

When the motor 6 is stopped, the pressure in the casing 2 is reduced, the pressure in the reservoir 45 is increased, the first check valve device 53 is closed, and the bypass hole 33 of the pressure equalizing device 30 is opened, so that the inside of the casing 2 is communicated with the reservoir 45 through the air suction pipe 13 until the pressure in the inside of the casing 2 is equal to the pressure in the reservoir 45. The pressure equalizing device 30 and the first check valve device 53 automatically control the opening and closing by pressure difference, and have the advantages of low cost, high reliability, no need of electric control and energy conservation.

The first check valve device 53 prevents gas from the reservoir 45 from flowing back to the evaporator 52. Optionally, the first check valve device 53 is a one-way valve or an electromagnetic switch valve to ensure that the gas in the evaporator 52 can enter the reservoir 45 through the first check valve device 53, and the high-pressure gas in the reservoir 45 cannot flow back to the evaporator 52.

Further, as shown in fig. 2, 5 to 6, the second check valve device 54 is provided in the exhaust pipe 3, and when the internal pressure of the housing 2 decreases, the second check valve device 54 closes. When the motor 6 is stopped, the second check valve device 54 prevents the high-pressure gas in the condenser 50 from flowing to the exhaust pipe 3, so as to ensure that the high-pressure gas in the casing 2 can enter the compression chamber 11 as soon as possible, and further ensure that the pressure in the casing 2 can be reduced to be equal to the pressure in the compression chamber 11 as soon as possible, so as to shorten the restart time of the compressor.

Optionally, the second check valve device 54 is a one-way valve or an electromagnetic switch valve to ensure that the gas in the exhaust pipe 3 can enter the condenser 50 through the second check valve device 54, and the high-pressure gas in the condenser 50 cannot flow back into the exhaust pipe 3.

The compression mechanism portion 5 includes: the compressor comprises a cylinder 10, a main bearing 20 and an auxiliary bearing 25, wherein the main bearing 20 is positioned at one end of the cylinder 10, the auxiliary bearing 25 is positioned at the other end of the cylinder 10, a compression cavity 11 is formed in the cylinder 10, an air suction pipe 13 is communicated with the compression cavity 11, and when the compressor normally operates, a refrigerant of a liquid accumulator 45 can enter the compression cavity 11 through the air suction pipe 13 and is compressed into high-pressure gas in the compression cavity 11 and then is discharged into a shell 3. When the compressor is stopped, the high-pressure gas in the shell 2 can enter the compression cavity 11 through the bypass hole 33 and then enter the liquid storage device 45 through the air suction pipe 13, so that the pressure in the shell 2 is reduced to be equal to the pressure in the liquid storage device 45 as soon as possible.

Referring to fig. 2, a muffler 23 is provided above the main shaft plate 21 of the main bearing 20, a high-pressure side opening end of the pressure equalizer 30 is opened in the muffler 23, and the muffler 23 has a muffler exhaust hole communicating with the internal cavity of the housing 2 (i.e., the space below the motor 6).

As shown in fig. 4, the pressure equalizing device 30 may include: a bypass valve 32, a spring 34, wherein the bypass valve 32 selectively connects the high pressure side opening end with the bypass hole 33 by using the pressure difference between the pressure in the housing 2 and the reservoir 45, in other words, the bypass valve 32 is used to open or close the bypass hole 33, and when the bypass valve 32 opens the bypass hole 33, the high pressure gas in the housing 2 can enter the suction pipe 13 through the bypass hole 33. Specifically, the high-pressure gas in the housing 2 can enter the air suction pipe 13 through the muffler exhaust hole, the high-pressure side open end of the bypass hole 33 and the bypass hole 33, and then enter the liquid reservoir 45 from the air suction pipe 13.

The spring 34 expands and contracts by a pressure difference between the pressure of the housing 2 and the reservoir 45, and the spring 34 moves the bypass valve 32 in a direction to open the bypass hole 33. In the embodiment shown in fig. 4, the spring 34 is a compression spring, and is located below the bypass valve 32, and always applies an upward thrust to the bypass valve 32. In some embodiments, not shown, the spring 34 may also be located above the bypass valve 32, always applying an upward pulling force on the bypass valve 32. The stopper 35 is used to limit the maximum moving distance of the bypass valve 32 and prevent the bypass valve 32 from falling off.

In the embodiments shown in fig. 2, 4-5, the pressure equalisation means 30 may be located on the main shaft plate 21 of the main bearing 20, although in some embodiments not shown, the pressure equalisation means 30 may also be located on the auxiliary shaft plate of the auxiliary bearing 25. Or the main shaft plate 21 and the auxiliary shaft plate are both provided with pressure equalizing devices 30.

When the rotary compressor 1 is stopped, high-pressure gas in the casing 2 leaks from the low-pressure compression chamber 11 to the intake pipe 13 via sliding surfaces such as the rolling piston 15 and the vane 16, and then diffuses into the accumulator 45. When the pressure difference between the casing 2 and the intake pipe 13 becomes small, the bypass hole 33 of the pressure equalizer 30 opens, the pressures of the casing 2 and the accumulator 45 rapidly become equal, and the first check valve device 53 and the second check valve device 54 close in the middle. The compressor 1 can be restarted in a short time and the pressure of the shell 2 is rapidly restored to a high pressure state before the stop. During the pressure increase of the casing 2, the pressure equalizing device 30 and the first and second

check valve devices

53 and 54 are opened.

The rotary compressor 1 according to the embodiment of the present invention has the following beneficial effects:

1) the restarting time can be greatly shortened in the air conditioner (schematically illustrated) for controlling the temperature of the air conditioner, and the fluctuation of the temperature of the air conditioner is greatly improved. In addition, the defrosting operation time can be shortened.

2) The necessary operation time becomes accurate, and a significant reduction in the compressor restart time can improve APF (annual energy efficiency).

3) The pressure equalizing device 30, the first check valve device 53, the second check valve device 54 and the like are automatically controlled by pressure difference, so that the cost is low, the reliability is high, electric control is not needed, and the energy is saved.

4) Inverter motors, whether operating at constant speed or variable speed, can be used.

5) The method can also be applied to rotary compressors such as rotary compressors and scroll compressors, double-cylinder type and horizontal type compressors.

A refrigeration cycle apparatus according to another aspect of the embodiment of the present invention includes the rotary compressor 1 of the above embodiment, as well as a condenser 50, an expansion valve 51, and an evaporator 52.

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, characterized by comprising:

a closed housing in which a motor and a compression mechanism section driven by the motor are built;

an exhaust pipe communicating with an interior of the housing;

the air suction pipe is connected with the compression cavity of the compression mechanism part;

the pressure equalizing device is provided with a bypass hole for communicating the inside of the shell with the air suction pipe;

a liquid storage device, one end of the liquid storage device is connected with the air suction pipe, the other end of the liquid storage device is connected with a first check valve device, when the motor stops, a bypass hole of the pressure equalizing device is opened, the first check valve device is closed, the gas in the shell flows into the air suction pipe or the liquid storage device, and the pressure equalizing device comprises: a bypass valve for opening or closing the bypass hole, and a spring for expanding and contracting by a pressure difference between the casing pressure and the reservoir, wherein a high-pressure side opening end of the bypass hole is positioned in a muffler of the compression mechanism;

and a second check valve device is arranged on the exhaust pipe, and when the internal pressure of the shell is reduced, the second check valve device is closed.

2. The rotary compressor of claim 1 wherein the first check valve arrangement is a one-way valve or an electromagnetic on-off valve.

3. The rotary compressor of claim 1 wherein the second check valve arrangement is a one-way valve or an electromagnetic on-off valve.

4. The rotary compressor of claim 1, wherein the compression mechanism comprises: the air suction pipe comprises an air cylinder, a main bearing and an auxiliary bearing, wherein the main bearing is located at one end of the air cylinder, the auxiliary bearing is located at the other end of the air cylinder, a compression cavity is formed in the air cylinder, and the air suction pipe is communicated with the compression cavity.

5. Rotary compressor according to claim 1 or 4 characterized in that the muffler has a muffler exhaust hole communicating with the inside of the shell.

6. The rotary compressor of claim 1, wherein the bypass valve selectively communicates the bypass hole with the suction pipe by a pressure difference between the casing pressure and the accumulator, and the spring moves the bypass valve in a direction to open the bypass hole.

7. A refrigerating cycle apparatus comprising the rotary compressor according to any one of claims 1 to 6.