CN112412793A

CN112412793A - Compressor and refrigeration cycle device

Info

Publication number: CN112412793A
Application number: CN201910786027.0A
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: 2021-02-26
Anticipated expiration: 2039-08-23
Also published as: CN112412793B

Abstract

The invention discloses a compressor and a refrigeration cycle device. The compressor includes a sealed high-pressure casing, a motor and a compression mechanism part driven by the motor are accommodated in the casing, an exhaust pipe with an opening to the casing is connected to an exhaust loop, a valve device in the exhaust loop includes a first valve body for preventing backflow from the exhaust loop to the casing, and a second valve body linked with the action of the first valve body and opening and closing a bypass loop, the bypass loop is communicated with a low-pressure gas loop connecting the valve device and an air suction hole of the compression mechanism part, when the motor stops, the bypass loop is opened by the second valve body, and when the motor operates, the bypass loop is closed by the second valve body. According to the compressor of the present invention, in an air conditioner for controlling the temperature of the air conditioner by the operation and stop of the compressor, the valve device can greatly reduce the stop time of the compressor, thereby greatly shortening the restart time.

Description

Compressor and refrigeration cycle device

Technical Field

The invention relates to the technical field of compressors, in particular to a compressor and a refrigeration cycle device. The present invention relates to a technique for greatly shortening the restart time of a compressor in which the pressure inside a casing is high. By the new technology, the comfort of the air conditioner, the APF (annual energy efficiency) and the like are improved.

Background

Compared with an inverter compressor which can freely change the rotating speed of a motor, the compressor with the rotating speed of the motor fixed at 50Hz or 60Hz needs to be frequently started and stopped repeatedly in order to control the room temperature through an air conditioner. However, if the restart time after the compressor is stopped is long as in the conventional art, the air conditioning comfort is poor and the APF is also deteriorated.

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 compressor to shorten the restart time of the compressor.

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

A compressor according to an embodiment of the present invention includes a sealed high-pressure casing, a motor and a compression mechanism section driven by the motor are housed in the casing, an exhaust pipe that opens a hole in the casing is connected to an exhaust circuit, a valve device in the exhaust circuit includes a first valve body that prevents a reverse flow from the exhaust circuit to the casing, and a second valve body that is linked to an operation of the first valve body and opens and closes a bypass circuit that communicates with a low-pressure gas circuit that connects the valve device and an intake hole of the compression mechanism section, the second valve body opens the bypass circuit when the motor is stopped, and the second valve body closes the bypass circuit when the motor is operated.

According to some embodiments of the present invention, a valve seat opened and closed by the first valve body is provided in the gas passage penetrating the second valve body.

According to some embodiments of the invention, the second valve body has a spring therein for moving the second valve body in the direction of the first valve body.

According to some embodiments of the invention, one end of the bypass circuit communicates with a reservoir connected to the low pressure gas circuit.

According to some embodiments of the invention, the first valve body is a thin plate valve for opening and closing the valve seat.

According to some embodiments of the present invention, the compression chamber of the compression mechanism portion includes at least a piston that revolves and a slide plate that reciprocates in association with the revolution of the piston.

Specifically, the valve device includes: the first valve body and the second valve body are arranged in the cylindrical pipe and are in sliding fit with the inner periphery of the cylindrical pipe, a condenser is arranged in the exhaust loop, the upper end of the cylindrical pipe is connected with a connecting pipe at the inlet of the condenser, and the lower end of the cylindrical pipe is connected with the exhaust pipe.

Furthermore, a second limiting structure and a third limiting structure are arranged in the cylindrical pipe, the second limiting structure is located above the third limiting structure, the second valve body is movably arranged between the second limiting structure and the third limiting structure up and down, and the spring is arranged between the second limiting structure and the third limiting structure.

According to some embodiments of the invention, a first limit structure is further disposed in the cylindrical pipe, the first limit structure is located above the second limit structure, and the first valve body is vertically movably disposed between the first limit structure and the second limit structure.

Further, the first valve body includes: the valve seat is provided with a trapezoidal hole matched with the trapezoidal end, the body is of a cylindrical structure, a plurality of wing parts are arranged on the outer peripheral surface of the body, the outer peripheries of the wing parts are in sliding fit with the inner peripheral surface of the cylindrical pipe, and a first gas channel is formed between every two adjacent wing parts and the inner peripheral surface of the cylindrical pipe.

According to other embodiments of the present invention, the thin plate valve comprises a flat valve body and a plurality of support arms located on an outer circumferential surface of the flat valve body, an area of the flat valve body is larger than an area of the exhaust holes of the valve seat, the second valve body has an upper extension section, the support arms are in sliding fit with an inner circumferential surface of the upper extension section, and a first air hole is formed between each two adjacent support arms and the inner circumferential surface of the upper extension section; a fourth limiting structure is arranged in the upper extending section, and the first valve body is movably arranged between the fourth limiting structure and the exhaust hole of the valve seat up and down.

According to some embodiments of the invention, the outer diameter sliding surface of the second valve body has a peripheral groove in which a plurality of second gas holes communicating with the gas passage of the second valve body are provided, the peripheral groove communicating with a side hole on the cylindrical pipe when the second valve body is in contact with the third stopper structure, the side hole communicating with the bypass circuit.

According to the compressor provided by the embodiment of the invention, in the air conditioner for controlling the temperature of the air conditioner through the running and stopping of the compressor, the first valve body and the second valve body act together, so that the stopping time of the compressor can be greatly reduced, and the restarting time is greatly shortened.

According to another aspect of the embodiment of the invention, the refrigeration cycle device comprises the compressor.

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

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 a refrigeration cycle apparatus incorporating the compressor of the present invention in operation;

FIG. 2 is a cross-sectional view of a design of a valve device;

FIG. 3 is a component view of the assembled valve device;

fig. 4 is a schematic view of a state where the compressor is stably operated by the driving of the motor;

FIG. 5 is an internal schematic view of the valve assembly when the motor is stopped, for example, due to the air conditioner temperature reaching a set temperature;

FIG. 6 is a schematic view of the outer peripheral groove of the second valve body aligned with the side hole to the center tube;

FIG. 7 is a schematic view of the high pressure gas of the housing flowing from the first end through the gas holes and the peripheral groove out of the bypass tube;

FIG. 8 is a schematic view of the spring action, pressing the second valve body upward;

FIG. 9 is a schematic illustration of the disengagement of the first valve body from the second valve body;

FIG. 10 is a graph of elapsed time after a compressor stop or restart versus operating pressure;

FIG. 11 is a schematic view of a first valve body and a second valve body of a second embodiment;

FIG. 12 is a schematic view of the first and second valve bodies of the second embodiment when the compressor is operating;

fig. 13 is a schematic view of the first valve body and the second valve body of the second embodiment when the compressor is stopped.

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.

The compressor to which the new technology is applied is generally a rotary compressor in which a pressure of a hermetic shell is high. For example, a rotary compressor in which a piston revolves and a vane reciprocates, a rotary compressor in which a piston and a vane rotate together, a scroll compressor including a fixed plate and a movable plate, and the like. The embodiment of the present invention discloses a technology of a rotary compressor which is most popular in a home air conditioner.

Example 1:

fig. 1 shows a refrigeration cycle apparatus including a compressor 1 according to the present invention in operation. The compressor 1 has a hermetic casing 2 in which a compression mechanism 5 and a motor 6 are housed and a bottom portion in which a lubricant oil 8 is housed. The outer periphery of the cylinder 40 of the compression mechanism 5 is fixed to the inner periphery of the casing 2 by spot welding, and a circular compression chamber 40a at the center of the cylinder 40 is sealed by a main bearing 50 and a sub bearing 53.

Crankshaft 55 is slidably fitted with main bearing 50 and sub bearing 53, and drives piston 45 to revolve in compression chamber 40 a. The slide 46 is reciprocated against the revolving piston 45. The motor 6 is composed of a stator 6a fixed to the inner periphery of the housing 2 by shrink fit and a rotor 6b fixed to the crankshaft 55.

A low-pressure accumulator 60 disposed outside the casing 2 has a casing suction pipe 61 connected to the upper portion thereof, and a center pipe 62 is provided in the center of the casing. The lower portion of the center pipe 62 is connected to a suction pipe 43, and the suction pipe 43 is pressed into a suction hole 41 that opens into the compression chamber 40 a.

Next, the flow of the refrigerant during operation of the compressor 1 will be described. The low-pressure gas (refrigerant) flowing from the center pipe 62 of the accumulator 45 to the suction pipe 43 flows into the compression chamber 40 a. The gas is compressed by the revolution of the piston 45 into high-pressure gas, is discharged from the gas discharge hole 50a into the sound deadening chamber 51, flows into the lower space of the motor 6, and flows into the upper space from the gap between the inside and the outside of the motor 6. During this period, most of the lubricating oil contained in the high-pressure gas is separated and joined to the lubricating oil 8 in the housing 2.

The exhaust pipe 3 provided at the center of the upper end of the casing 2 is connected to a condenser 70 of the refrigeration cycle apparatus. The condenser 70 is connected in this order of an expansion valve 71, an evaporator 72, and a liquid reservoir 60. In addition, the expansion valve 71 may be a capillary tube.

The upper part of the exhaust pipe 3 is connected to a valve device 10, which is a key component of the present invention. The cylindrical pipe 11 of the valve device 10 has a side connected to the bypass pipe 18 and the other end connected to the casing suction pipe 61 of the accumulator 60.

When the compressor 1 is operated stably, the internal pressure of the casing 2 is high (Pd), and the pressure of the condenser 70 is high equal to the internal pressure of the casing 2 due to the high-pressure gas flowing out of the gas discharge pipe 3, and the gas refrigerant of the condenser 70 is cooled by the fan to become a liquid refrigerant, and the pressure is reduced by the expansion valve 71.

Thereafter, the gas refrigerant evaporated in the evaporator 72 becomes a low pressure (Ps) and flows into the accumulator 60. At this time, a part of the low-pressure liquid refrigerant that cannot be evaporated in the evaporator 72 flows into the accumulator 60. Thereafter, the low-pressure gas refrigerant in the accumulator 60 flows into the compression chamber 40a, and the refrigerant is circulated.

Fig. 2 is a cross-sectional view of the design of the valve device 10, and fig. 3 is a view of the components that make up the valve device 10. The cylindrical pipe 11 is composed of a center pipe 11A provided at the center, and a first end pipe 11A and a second end pipe 11b which are reduced in diameter at both ends thereof. The first valve body 20 and the second valve body 30 are disposed inside the center tube 11A, and are slidably fitted to the inner circumference of the center tube 11A.

The a stopper 25, the B stopper 26 and the C stopper 27 are respectively installed in the stopper groove 25a, the stopper groove 26a and the stopper groove 27a of the inner periphery of the circular tube 11A. The first valve body 20 can move up and down between the a stopper 25 and the B stopper 26. A second valve body 30 and a spring 33 (compression spring) are provided between the B stopper 26 and the C stopper 27, and the second valve body 30 can move up and down between the above 2 stoppers.

The spring 33 installed in the spring chamber 30C of the second valve body 30 and the inner diameter groove 27b of the C stopper 27 constantly presses the second valve body 30. Therefore, during the stop of the compressor 1, the upper end of the outer peripheral sliding surface 31 of the second valve body 30 is stationary at the B stopper 26.

The first valve element 20, which operates as a check valve, is composed of a cylindrical main body 21a, a

trapezoidal end

21b, and 3 wing portions 21c integrally formed on the outer periphery of the main body 21 a. The outer periphery of the 3 wings 21c is in sliding fit with the inner periphery of the center tube 11A.

The second valve body 30 has a trapezoidal hole 30a opened and closed by the trapezoidal end 21b of the first valve body 20 at an upper end thereof, a cylindrical chamber 30b communicating with the trapezoidal hole 30a at a center of the second valve body 30, and a spring chamber 30c communicating with the cylindrical chamber 30 b. Therefore, the high-pressure gas flowing in from the first end pipe 11a flows in the order of the spring chamber 30c, the cylindrical chamber 30b, and the trapezoidal hole 30 a.

The outer diameter sliding surface 31 of the second valve body 30 has an outer

peripheral groove

31a and 4 air holes 31b communicating the outer peripheral groove 31a and the cylindrical chamber 30 b. When the second valve body 30 is lowered and the lower end surface of the second valve body 30 is stationary above the C stopper 27, the outer peripheral groove 31A communicates with the side surface hole 13 of the center pipe 11A. At this time, since the trapezoidal hole 30a is closed by the trapezoidal end 21b of the first valve body 20, the high-pressure gas of the cylinder chamber 30b and the high-pressure gas of the housing 2 can flow out of the bypass pipe 18.

The first end pipe 11a is connected to the exhaust pipe 3 fixed to the casing 2, the second end pipe 11b is connected to the connection pipe 4, and the connection pipe 4 is fixed to the inlet of the condenser 70. The left end of the bypass pipe 18 is connected to the side hole 13 on the side of the center pipe 11A, and the right open end of the bypass pipe 18 is connected to the casing air suction pipe 61 of the reservoir 60.

For reference, a copper pipe excellent in formability is used for the cylindrical pipe 11. Furthermore, the 3 sets of limiter and limiter slots may be replaced by circular convex protrusions formed from copper tubing. The first valve element 20 and the second valve element 30 are integrally molded from a synthetic resin having excellent heat resistance, refrigerant resistance, and oil resistance.

Next, the operation of the valve device 10 at the time of standstill or restart of the compressor 1 in operation will be described with reference to fig. 4 to 9. The first end pipe 11a and the second end pipe 11b in these figures are connected to the exhaust pipe 3 and the connection pipe 4 shown in fig. 1, respectively.

Fig. 4 shows a state where the compressor 1 is stably operated by the driving of the motor 6. The high-pressure gas (pressure Pd) discharged from the exhaust pipe 3 passes through the inner space of the second valve element 30 from the center hole 27C of the C stopper 27 from the first end pipe 11a, and then passes through the second end pipe 11b from the outer peripheral gap of the main body 21a of the first valve element 20 from the trapezoidal hole 30 a. And then out of the condenser 70 so that the condenser 70 maintains a high pressure. In this stroke, the first valve body 20 is at rest at the a stopper 25, and the gap between the trapezoidal end 21b and the trapezoidal hole 30a becomes maximum.

Fig. 5 shows the inside of the valve device 10 when the motor 6 is stopped due to the air-conditioning temperature reaching a set temperature, for example. If the expansion valve 71 is closed in conjunction with the stop operation of the motor 6, the high-pressure gas (Pd) of the condenser 70 passes through the second end pipe 11b and the first end pipe 11a of the valve device 10 and starts to flow out to the casing 2, the pressure of which is slightly lowered.

At this moment, the first valve body 20 descends, and the trapezoidal end 21b abuts against and closes the trapezoidal hole 30 a. Therefore, since the first valve body 20 is integrated with the second valve body 30, the communication between the second end pipe 11b and the first end pipe 11a is cut off. That is, the first valve element 20 functions not only as a check valve but also descends in the direction of the first end pipe 11a together with the second valve element 30.

The bottom surface of the lowered second valve body 30 rests on the C stopper 27 of the spring 33 shown in fig. 6. At this time, the outer peripheral groove 31A of the outer peripheral sliding surface 31 of the second valve body 30 coincides with the side surface hole 13 that is bored in the side surface of the center pipe 11A.

Therefore, the 4 gas holes 31b that open into the cylindrical chamber 30b communicate with the bypass pipe 18 that connects the side surface holes 13 through the outer peripheral groove 31 a. The high-pressure gas (Pd-) of the housing 2 flows out of the bypass pipe 18 from the first end pipe 11a through the gas hole 31b and the outer circumferential groove 31 a.

As a result, the high-pressure gas in the casing 2 is rapidly reduced to about 8 to 15 seconds before reaching the pressure of the reservoir 60. That is, the state of fig. 7 is changed, and the pressure at that time is a low pressure (Ps +) which is slightly raised. On the other hand, the high pressure (Pd) in the condenser 70 is slightly lowered by heat release, and becomes Pd-.

In the stroke shown in fig. 5 to 6, the phenomenon in which the pressure of the casing 2 gradually decreases is caused by a gas leakage phenomenon in which high-pressure gas in the casing 2 leaks from the sliding surface (gap 5 to 10 μm) between the piston 45 and the vane 46 to the low-pressure compression chamber 40 a. Further, cooling of the internal gas of the motor 6 and the housing 2 during the stop is also a cause of the pressure reduction.

When the low pressure of the casing 2 is equal to the low pressure of the accumulator 60, the activation of the motor 6 activates the compressor 1. Thereafter, if the compressor 1 is rapidly restarted, the amount of gas discharged from the compression chamber 40a becomes maximum. However, since the pressure is low, the second valve body 30 does not operate, and a part of the exhaust gas flows out from the bypass pipe 18 to the accumulator 60, so that the pressure of the housing 2 slowly rises.

However, if the spring 33 is actuated to press the second valve body 30, as shown in fig. 8, the bypass pipe 18 is closed, and thus the pressure increase rate is restored, and the high pressure of the housing 2 is rapidly increased. When the pressures of the first end pipe 11a and the second end pipe 11b are equal, the first valve body 20 is disengaged from the second valve body 30, and the state of fig. 9 is obtained. I.e. back to the state of fig. 4. As a result, the pressure in the casing 2 and the condenser 70 becomes equal, the pressure rises, and the operation can be transitioned to a stable operation.

Thus, in example 1 of the present invention,

(1) the first valve body 20 cuts off the connection of the casing 2 and the condenser 70 immediately after the compressor 1 is stopped by the check valve effect, and thus the pressure-reducing time and the pressure-increasing time of the casing 2 of the compressor 1 are greatly shortened.

(2) The second valve body 30 can be connected or disconnected with the bypass pipe 18 of low pressure by the effect of connecting the first valve body 20 and the second valve body 30. As a result, the pressure reducing time of the casing 2 can be further shortened.

Next, the reduction of the restart time of the compressor, which is the object of embodiment 1, will be described. The restart time refers to a time from when the motor of the compressor is stopped until the compressor can be restarted during operation, and a time from when the motor of the compressor is started until the pressure of the compressor reaches the pressure of the condenser. In addition, like embodiment 1, in the case where the first valve element 20 of the check valve is used in the exhaust circuit, the time until the first valve element 20 can be opened after being closed is the restart time.

In fig. 10, the horizontal axis represents elapsed time (minutes) after the compressor is stopped or restarted, and the vertical axis represents operating pressure (MPaG). First and second are pressure changes after the compressor is stopped and pressure changes after the compressor is restarted, and their attainment times, respectively, in the compressor 1 including the valve device 10. For comparison, the pressure change after the stop of the conventional compressor is shown. The compressor 1 and the conventional compressor are mounted on a household air conditioner, the used refrigerant is R410A, the high pressure (Pd) before the operation stop is 3.0MPaG, and the low pressure (Ps) is 0.7 MPaG.

In fig. 10, Δ 1 represents the time (restart possible time) when the high pressure and the low pressure become equal after the compressor 1 is stopped, and Δ 2 represents the time (restart time) when the first valve body 20 is opened after the compressor 1 is restarted. A and B represent the time that the bypass pipe 18 is closed and open, respectively. A 1 represents the time until the high pressure and the low pressure become equal after the conventional compressor is stopped.

In (1), when the compressor 1 is stopped, Pd decreases Ps and increases. Thereafter, about 16 seconds passes, the bypass pipe 18 is opened, and thus the high pressure (Pd) rapidly decreases and the low pressure (Ps) rapidly increases. As a result, the pressure reached the equilibrium pressure (1.6MPaG) after about 30 seconds from the stop of the compressor. At this instant, the compressor 1 may be restarted.

If the compressor 1 is started after 10 seconds thereof, since the bypass pipe 18 is in an open state, although the pressure change of the high pressure (Pd) and the low pressure (Ps) is slightly slow, the bypass pipe 18 is gradually closed until it is completely closed after 24 seconds, and the rise of the high pressure (Pd) and the fall of the low pressure (Ps) are accelerated. After 36 seconds from the start-up, the first valve body 20 opens the trapezoidal hole 30a, and the high-pressure gas of the housing 2 flows out of the condenser 70 (start-up completion). Therefore, at the operating pressure of fig. 10, the time from the stop of the compressor 1 to the completion of the restart is about 30 seconds + about 36 seconds, which is about 66 seconds.

In addition, since the time from the operation stop of the conventional rotary compressor to the time when the high pressure (Pd) is the same as the low pressure (Ps) is 2 minutes 43 seconds (163 seconds), if the operation stop time is compared with only the compressor 1 of the embodiment 1, the compressor 1 is 18.4% of the conventional compressor.

The main reasons for the time required for the operation stop to be greatly shortened are (1) the compressor 1 including the bypass pipe 18 and the second valve body 30 for opening and closing the bypass pipe 18, and (2) the compressor 1 including the first valve body 20 for cutting off the connection with the condenser 70 in the discharge pipe. In addition, since the spring constant of the spring 33 related to the operation of the second valve body 30 is related to the restart time of the compressor 1, it is necessary to optimize the spring constant.

Example 2:

in embodiment 1, the first valve body 20 is a check valve having a general shape, and as shown in fig. 11, the flat valve 22 is used as the second valve body 30 instead of the first valve body 20, so that the design of the valve device 10 can be simplified and downsized.

In fig. 11, the exhaust hole 35 is opened in the cylindrical chamber 32 added to the upper end extension of the outer peripheral sliding surface 31. The flat valve 22 for opening and closing the exhaust hole 35 has 4 air holes 22a in its outer diameter. The valve stopper 28 is installed in a circumferential groove at the upper end of the cylindrical chamber 32, the valve stopper 28 may be a flat plate, and the valve stopper 28 is provided with an opening so that the opening of the valve stopper 28 is aligned with the outer circumferential gas hole 28a, thereby ensuring that the gas flowing out of the outer circumferential gas hole 28a can reach the second end pipe 11b through the opening of the valve stopper 28.

In fig. 12, the high-pressure gas passing through the first end pipe 11a from the housing 2 flows out to the second end pipe 11b through the exhaust hole 35 and the outer periphery of the flat valve 22 closely attached to the lower side of the valve stopper 28. When the compressor 1 is stopped, the flat valve 22 closes the discharge hole 35 as shown in fig. 13.

Thus, the flat valve 22 functions as a check valve and can exhibit the same operation and effect as the first valve element 20 of embodiment 1. In addition, the flat valve 22 may be the same material and thickness as the compressor discharge valve design.

A compressor according to an embodiment of the present invention will be described in detail with reference to fig. 1 to 13.

Referring to fig. 1, a compressor 1 according to an embodiment of the present invention is a high pressure shell type compressor, and the compressor 1 may include: the compressor comprises a shell 2, a motor 6, a compression mechanism part 5, an exhaust pipe 3 and a bypass circuit 18, wherein the motor 6 is arranged in the shell 2, the compression mechanism part 5 is arranged in the shell 2, and the compression mechanism part 5 is driven by the motor 6. Alternatively, the motor 6 may be of a fixed speed type or a variable speed type.

Specifically, the compression mechanism 5 includes a cylinder 40, a main bearing 50, and an auxiliary bearing 53, the cylinder 40 has a compression chamber 40a therein, the piston 45 is fitted over a crankshaft 55, the crankshaft 55 is driven by the motor 6, the slide piece 46 abuts against the outer peripheral surface of the piston 45, and the slide piece 46 reciprocates. The wall of the compression cavity 40a is provided with a suction hole 12, the liquid reservoir 60 is connected with the suction hole 41 through a suction pipe 43, and the low-pressure refrigerant in the liquid reservoir 60 can be conveyed into the compression cavity 40a through the suction pipe 43 and the suction hole 41.

One end of the exhaust pipe 3 communicates with the inside of the casing 2, the other end of the exhaust pipe 3 is connected to the exhaust circuit through the valve device 10, one end of the bypass circuit 18 (i.e., the bypass pipe 18) is connected to the valve device 10, the other end of the bypass circuit 18 is connected to the accumulator 60, i.e., the accumulator 60 is connected to the low-pressure gas circuit, the other end of the bypass circuit 18 communicates with the inside of the accumulator 60, and the suction pipe 43 of the accumulator 60 communicates with the compression chamber 40a of the compression mechanism portion 5. The bypass circuit 18 communicates with a low-pressure gas circuit that connects the valve device 10 and the suction hole 41 of the compression mechanism portion 5, in other words, when the bypass circuit 18 is opened, the valve device 10 and the suction hole 41 of the compression mechanism portion 5 communicate, and at this time the accumulator 60 and the valve device 10 are both connected to the low-pressure gas circuit.

Referring to fig. 2 to 9, the valve device 10 includes a first valve body 20 and a second valve body 30, and the first valve body 20 prevents the reverse flow of the exhaust circuit to the exhaust pipe 3. The second valve body 30 opens the bypass circuit 18 when the motor 6 is stopped, and the second valve body 30 closes the bypass circuit 18 when the motor 6 is operated.

Specifically, referring to fig. 3, the valve device 10 may include a cylindrical pipe 11, the first valve body 20 and the second valve body 30 are disposed inside the cylindrical pipe 11, and both the first valve body 20 and the second valve body 30 are slidably fitted to an inner circumference of the cylindrical pipe 11, a condenser 70 is provided in the exhaust circuit, an upper end of the cylindrical pipe 11 is connected to a connection pipe 4 fixed at an inlet of the condenser 70, and a lower end of the cylindrical pipe 11 is connected to the exhaust pipe 3.

Further, the second valve body 30 has a second gas flow passage, which is a gas passage penetrating the second valve body 30, and the second gas flow passage has a valve seat opened and closed by the first valve body 20, and the second valve body 30 has a second gas discharge hole 30a opened in the valve seat, and the first valve body 20 opens and closes the second gas discharge hole 30 a.

The second valve body 30 has a spring 33 for moving the second valve body 30 in the direction of the first valve body 20.

Further, a second limiting structure 26 and a third limiting structure 27 are arranged in the cylindrical tube 11, the second limiting structure 26 is located above the third limiting structure 27, the second valve body 30 is arranged between the second limiting structure 26 and the third limiting structure 27 in a vertically movable manner, and the spring 33 is located between the second limiting structure 26 and the third limiting structure 27. In the embodiment shown in fig. 4, the spring 33 is located between the second valve body 30 and the third position limiting structure 27, and the spring 33 is a compression spring. In other embodiments, not shown, the spring 33 may be located between the second limiting structure 26 and the second valve body 30, and the spring 33 is an extension spring that pulls the first valve body 20 toward the second valve body 30.

As shown in fig. 1 to 2, when the high-pressure gas in the housing 2 is discharged to the exhaust pipe 3 through the valve device 10, the high-pressure gas pushes the second valve body 30 to move upward, and the second stopper structure 26 serves to limit the uppermost position of the second valve body 30. When the gas in the housing 2 no longer pushes the second valve body 30 upward, the second valve body 30 will move downward due to gravity, and the third limiting structure 27 is used to limit the lowest position of the second valve body 30, so as to prevent the second valve body 30 from falling out of the cylindrical tube 11.

A first limit structure 25 is also arranged in the cylindrical pipe 11, the first limit structure 25 is positioned above the second limit structure 26,

the first valve body 20 is movably disposed between the first limit structure 25 and the second limit structure 26 up and down, so as to prevent the first valve body 20 from being removed from the cylindrical tube 11.

Further, as shown in fig. 3, the first valve body 20 includes: the second exhaust hole 30a of the second valve body 30 is a trapezoidal hole 30a matched with the trapezoidal end 21b, the body 21 is of a cylindrical structure, a plurality of wing parts 21c are arranged on the outer peripheral surface of the body 21, the outer periphery of each wing part 21c is in sliding fit with the inner peripheral surface of the cylindrical tube 11, and a first gas channel is formed between two adjacent wing parts 21c and the inner peripheral surface of the cylindrical tube 11.

When the trapezoidal end 21b is separated from the trapezoidal hole 30a, as shown in fig. 4 and 9, the high-pressure gas in the housing 2 can reach the exhaust pipe 3 through the second gas flow passage and the first gas flow passage.

In other embodiments of the present invention, as shown in fig. 11-13, the first valve body is a flat valve 22, the flat valve 22 is a thin plate valve, and the flat valve 22 includes a flat valve body and a plurality of arms located on the outer periphery of the flat valve body, and the area of the flat valve body is larger than that of the second exhaust hole 30a, so as to ensure that the second exhaust hole 30a can be completely closed when the first valve body 20 contacts the second valve body 30.

The second valve body 30 has an upper extension section, the support arms are in sliding fit with the inner peripheral surface of the upper extension section, and a first air hole 22a is formed between two adjacent support arms and the inner peripheral surface of the upper extension section; a fourth limiting structure 28 is arranged in the upper extending section, and the first valve body is movably arranged between the fourth limiting structure 28 and the second exhaust hole 30a up and down.

Referring to fig. 1 to 9 and 11 to 13, the outer diameter sliding surface of the second valve body 30 has an outer circumferential groove 31a, a plurality of second air holes 31b communicating with the second air flow passage are provided in the outer circumferential groove 31a, and when the second valve body 30 contacts the third stopper structure 27, the outer circumferential groove 31a communicates with the side surface hole 13 of the cylindrical pipe 11, and the side surface hole 13 communicates with the bypass circuit 18.

The valve device 10 is connected to the exhaust pipe 3 that opens into the high-pressure casing 2, and the valve device 10 includes a first valve body 20 having a check valve function, and a second valve body 30 that opens and closes the bypass pipe 18 in conjunction with the first valve body 20. When the compressor 1 is operated, the first valve body 20 is opened and the second valve body 30 closes the bypass pipe 18. When the compressor 1 is stopped, the first valve body 20 and the second valve body 30 are coupled to each other, and the reverse flow from the condenser 70 to the exhaust pipe 3 is stopped. At the same time, the bypass line 18 opens due to the sliding fit inside the valve assembly 10. At this time, since the high-pressure gas of the casing 2 flows out of the low-pressure accumulator 60 through the bypass pipe 18, the restart time of the compressor 1 is shortened.

The invention has the following effects:

1) in an air conditioner (schematically illustrated) for controlling the temperature of an air conditioner by On/Off (operation and stop) of a high-pressure shell compressor, the stop time of the compressor can be reduced to about 18% of the conventional time, and the restart time can be significantly shortened.

2) By this effect, the variation in air conditioning temperature is reduced, and comfort and APF (annual energy efficiency) can be improved.

3) Because no electric valve is used, the control is easy and the cost is low.

4) The valve device 10 of the present invention can be added to a high-pressure shell compressor equipped with an inverter motor for varying the motor speed.

5) The valve device 10 can be added without changing the internal design of the conventional high-pressure shell compressor.

6. It can be used in double-cylinder and horizontal compressors.

A refrigeration cycle apparatus according to another aspect of the embodiment of the present invention includes a condenser 70, an expansion device 71, an evaporator 72, and an accumulator 60, and the compressor 1 of the above 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 compressor, comprising:

a sealed high-pressure housing, in which a motor and a compression mechanism part driven by the motor are housed,

an exhaust pipe that opens a hole in the casing is connected to an exhaust circuit, a valve device in the exhaust circuit includes a first valve body that prevents a reverse flow from the exhaust circuit to the casing, and a second valve body that is interlocked with an operation of the first valve body and opens and closes a bypass circuit, the bypass circuit communicates with a low-pressure gas circuit that connects the valve device and an intake hole of the compression mechanism portion, the bypass circuit is opened by the second valve body when the motor is stopped, and the bypass circuit is closed by the second valve body when the motor is operated.

2. The compressor according to claim 1, wherein a valve seat opened and closed by the first valve body is provided in a gas passage passing through the second valve body.

3. The compressor of claim 1, wherein the second valve body has a spring therein that moves the second valve body in the direction of the first valve body.

4. The compressor of claim 1, wherein one end of the bypass circuit communicates with an accumulator connected to the low pressure gas circuit.

5. The compressor of claim 2, wherein the first valve body is a thin plate valve that opens and closes the valve seat.

6. A compressor according to claim 3, wherein the valve means comprises: the first valve body and the second valve body are arranged in the cylindrical pipe and are in sliding fit with the inner periphery of the cylindrical pipe, a condenser is arranged in the exhaust loop, the upper end of the cylindrical pipe is connected with a connecting pipe at the inlet of the condenser, and the lower end of the cylindrical pipe is connected with the exhaust pipe.

7. The compressor of claim 6, wherein a second limit structure and a third limit structure are arranged in the cylindrical pipe, the second limit structure is located above the third limit structure, the second valve body is movably arranged between the second limit structure and the third limit structure up and down, and the spring is arranged between the second limit structure and the third limit structure.

8. The compressor of claim 7, wherein a first limit structure is further disposed in the cylindrical pipe, the first limit structure is located above the second limit structure, and the first valve body is vertically movably disposed between the first limit structure and the second limit structure.

9. The compressor of claim 2, wherein the first valve body comprises: the valve seat is provided with a trapezoidal hole matched with the trapezoidal end, the body is of a cylindrical structure, a plurality of wing parts are arranged on the outer peripheral surface of the body, the outer peripheries of the wing parts are in sliding fit with the inner peripheral surface of the cylindrical pipe, and a first gas channel is formed between every two adjacent wing parts and the inner peripheral surface of the cylindrical pipe.

10. The compressor of claim 5, wherein the thin plate valve comprises a flat valve body and a plurality of support arms located on the outer peripheral surface of the flat valve body, the area of the flat valve body is larger than that of the exhaust hole of the valve seat, the second valve body has an upper extension section, the support arms are in sliding fit with the inner peripheral surface of the upper extension section, and a first air hole is formed between two adjacent support arms and the inner peripheral surface of the upper extension section;

a fourth limiting structure is arranged in the upper extending section, and the first valve body is movably arranged between the fourth limiting structure and the exhaust hole of the valve seat up and down.

11. The compressor of claim 7, wherein the outer diameter sliding surface of the second valve body has a peripheral groove, the peripheral groove having a plurality of second gas holes therein communicating with the gas passage of the second valve body, the peripheral groove communicating with a side hole on the cylindrical tube when the second valve body contacts the third stopper structure, the side hole communicating with the bypass circuit.

12. A refrigeration cycle apparatus comprising the compressor of any one of claims 1 to 11.