KR20180094408A - High pressure compressor and refrigerating machine having the same - Google Patents

Abstract

The present invention provides a high pressure compressor and a freezing cycle machine having the same to be quickly restarted after turned off. The high pressure compressor includes: a compression unit provided in an inner space of a casing, provided with a compression space for compressing a refrigerant, and provided with a discharge port for guiding the refrigerant compressed in the compression space to the inner space of the casing; a discharge valve provided to selectively open and close the discharge port according to a difference between an inner space pressure of the casing and a compression space pressure of the compression unit; a first valve for preventing the refrigerant discharged from the inner space of the casing from flowing back into the inner space of the casing; a bypass pipe connecting the inner space of the casing to a suction side of the compression unit; and a second valve disposed in the casing and connected to the bypass pipe to selectively open and close the bypass pipe while moving between a first position and a second position in accordance with the difference between the inner pressure of the casing and a discharge side pressure of the compression unit.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a high pressure compressor,

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a compressor, and more particularly, to a high-pressure compressor in which an internal space of a casing forms a high-pressure portion and a refrigeration cycle apparatus having the same.

Generally, a compressor is applied to a vapor compression type refrigeration cycle such as a refrigerator or an air conditioner (hereinafter abbreviated as a refrigeration cycle).

The compressor can be classified into indirect suction type and direct suction type according to the method of sucking the refrigerant into the compression chamber. In the indirect suction type, the refrigerant circulating in the refrigeration cycle flows into the internal space of the compressor casing and is sucked into the compression chamber. The direct suction type is a type in which the refrigerant is directly sucked into the compression chamber, unlike the indirect suction type. The indirect suction type is classified into a low pressure type compressor and the direct suction type is classified into a high pressure type compressor.

As the refrigerant flows into the inner space of the compressor casing first, the liquid refrigerant or oil is filtered in the inner space of the compressor casing, so that no separate accumulator is provided. On the other hand, in the high pressure type compressor, in order to prevent liquid refrigerant or oil from flowing into the compression chamber, an accumulator is usually provided on the suction side rather than the compression chamber.

In such a high-pressure compressor, the inner space of the casing forms a high-pressure portion which is a discharge space, and the inner space of the accumulator forms a low-pressure portion. Therefore, when the power of the refrigeration cycle is turned off during operation, the difference between the suction pressure and the discharge pressure of the compressor becomes large, so that the compressor can not be instantaneously restarted. Therefore, the air conditioner using most of the high-pressure type compressors keeps the operation stop for a certain period of time after the operation of the compressor is stopped (OFF), thereby ensuring the pneumatic pressure time for adjusting the suction pressure and the discharge pressure within a certain range Called "three-minute resumption", which is a so-called "three-minute restart".

Particularly, in the unitary air conditioner field in North America, the fan of the refrigeration cycle is operated during the additional operation such as restarting the compressor for 3 minutes when the compressor is stopped, so that the differential pressure generated during the operation of the refrigeration cycle apparatus reaches the normal pressure By using latent heat, a method of maximizing the efficiency of the refrigeration cycle apparatus is used.

However, if the time for which the differential pressure of the refrigeration cycle apparatus reaches the pressure (hereinafter, referred to as the differential pressure interval or the pressure required time) becomes long, the oil in the compressor flows out through the gap between the members to lower the oil surface, This makes it difficult to apply the high-pressure compressor to a refrigeration apparatus such as an air conditioner. That is, due to the difference between the suction pressure and the discharge pressure, the oil in the internal space of the casing flows out through the clearance between the members to the accumulator having a relatively low pressure as compared with the internal space of the casing, Is lowered. Particularly, the rotary compressor is not restarted even when the differential pressure between the suction pressure and the discharge pressure is as small as about 1 kgf / cm 2. Therefore, once the compressor is stopped, the compressor is not easily restarted. However, if the input power is continuously supplied even when the compressor is not restarted due to the differential pressure, an overload is generated in the motor. As a result, the overload protector (OLP) Therefore, considering the oil outflow, the compressor can not be operated for a long time to reach the pneumatic pressure, and accordingly, the rotary compressor having a short time required for the pneumatic pressure can not be applied to the refrigeration cycle apparatus using the latent heat at the time required for the pneumatic pressure. Therefore, there is a problem that it is difficult to apply a rotary compressor, which is a high-pressure compressor, to an air conditioner or the like in a region where efficiency of the refrigeration cycle apparatus is important.

Instead, in a unitary air conditioner employing a high-pressure compressor, a method of installing an orifice between the condenser and the evaporator so as to quickly reach the pressure from the differential pressure can be applied. However, it is also impossible to use the latent heat of the differential pressure section if the orifice is used to shorten the time required for the pneumatic pressure, which is also disadvantageous in terms of efficiency, making it difficult to apply a high pressure compressor to a refrigerating device such as an air conditioner there was.

In addition, when the conventional rotary compressor is applied, since the restarting of the compressor is not smooth after the refrigeration cycle is stopped, the overload preventing device for preventing the overload of the motor is repeatedly operated, There is a problem that the reliability of the compressor is deteriorated because the prevention device is damaged or burned out due to overheating of the motor.

In view of these problems, a solenoid valve is provided in the middle of the bypass pipe to connect the discharge side and the suction side of the compressor with the bypass pipe. When the compressor is stopped, the solenoid valve is opened to bypass the refrigerant on the discharge side to the suction side So that the pneumatic pressure can be achieved. However, in this case, separate power for operating the solenoid valve is required, and a separate control unit for selectively operating the solenoid valve is required, which increases the manufacturing cost and decreases the reliability due to malfunction There was a problem. In addition, since the solenoid valve is weak in high temperature due to its characteristics, it is installed outside the casing, which is limited in the installation of the casing of the compressor, which not only increases the size of the compressor but also exposes to the risk of damage during transportation.

An object of the present invention is to provide a high-pressure compressor which can be quickly restarted when the refrigeration cycle apparatus is turned off and then restarted, and a refrigeration cycle apparatus having the same.

It is a further object of the present invention to provide a refrigeration cycle apparatus and a refrigeration cycle apparatus that can perform a pneumatic operation for relieving a differential pressure between a suction pressure and a discharge pressure at the same time as a compressor is stopped, And to provide a refrigeration cycle apparatus having the same.

It is another object of the present invention to provide a refrigeration cycle control apparatus and a refrigeration cycle control method for a refrigeration cycle apparatus in which when the refrigeration cycle apparatus is turned off and the compressor is stopped, a pneumatic operation for eliminating a differential pressure between a suction pressure and a discharge pressure is performed at an appropriate time, And to provide a refrigeration cycle apparatus having the same.

It is another object of the present invention to provide a high-pressure compressor and a refrigeration cycle apparatus having the refrigeration cycle apparatus, which enable the refrigeration cycle apparatus to perform heat exchange in a state that the refrigeration cycle apparatus is turned off and the compressor is stopped.

It is another object of the present invention to provide a refrigeration cycle apparatus capable of quickly restarting a compressor of a refrigeration cycle apparatus to prevent damage to the overload prevention apparatus and prevent the motor from being overheated and burned, And a refrigeration cycle device having the same.

It is another object of the present invention to provide a high-pressure compressor having a pressure-reducing device which can reduce the manufacturing cost and increase the reliability of the compressor by eliminating the use of the solenoid valve and can prevent the compressor from being damaged during operation, Device.

In order to achieve the object of the present invention, a mechanical opening / closing valve operated according to a difference between the pressure filled in the inner space of the casing and the pressure discharged from the compression unit is used to apply a pressure between the inner space of the casing and the compression space of the compression unit, State compressor and a refrigeration cycle apparatus having the high-pressure compressor can be provided.

Here, the mechanical opening / closing valve may further include an elastic member in consideration of a case where the pressure difference is small.

A check valve may be provided in the discharge pipe of the casing to prevent the refrigerant discharged from the internal space of the casing through the discharge pipe toward the condenser to flow back into the internal space of the casing.

In order to achieve the object of the present invention,

A driving motor provided in an inner space of the casing; A compression unit disposed in an inner space of the casing and having a compression space for compressing the refrigerant and having a discharge port for guiding the refrigerant compressed in the compression space to the inner space of the casing; A discharge valve provided to selectively open and close the discharge port according to a difference between an internal space pressure of the casing and a compression space pressure of the compression unit; A first valve for preventing the refrigerant discharged from the internal space of the casing from flowing back to the internal space of the casing; A bypass pipe connecting between an inner space of the casing and a suction side of the compression section; And a control unit connected to the bypass pipe in the casing and selectively opening and closing the bypass pipe while moving between a first position and a second position in accordance with a difference between an internal pressure of the casing and a discharge- And a second valve, wherein the high-pressure compressor is provided with a high-pressure compressor.

Here, the second valve may be configured to block the bypass pipe when a compression load is generated in the compression unit, and to open the bypass pipe when the compression load is removed from the compression unit.

The second valve is provided with a valve space, and one side of the valve space is formed with a first hole communicating with the discharge side of the compression unit, and the other side of the valve space is communicated with the second space communicating with the inner space of the casing And a third hole communicating with the bypass pipe is formed between the first hole and the second hole; And a valve plate inserted in the valve space of the valve housing and moving between the first position and the second position according to a difference between a pressure supplied to the first hole and a pressure supplied to the second hole have.

The cross-sectional area of the second hole may be greater than or equal to the cross-sectional area of the first hole.

The third hole may be formed in a direction crossing the center line of the first hole or the second hole, and the inner diameter of the third hole may be formed to be smaller than or equal to the thickness of the valve plate in the moving direction.

The third hole may be formed to be closed together with the valve plate at a position where the second hole is closed.

In addition, a valve spring may be further provided at one side of the valve plate to provide an elastic force to the valve plate.

The valve spring may be provided at the second hole side with the valve plate interposed therebetween.

Here, the second valve may be provided between the driving motor and the compression unit.

The discharge port is provided with a plurality of discharge ports so that the refrigerant compressed in the compression section is discharged in both directions with respect to the axial direction with reference to the compression section, and the refrigerant discharged to one of the discharge ports, A plurality of refrigerant passages are formed so as to be combined with the refrigerant discharged from the discharge port, and the second valve may be provided so as to communicate with any one of the plurality of refrigerant passages.

The inner diameter of the refrigerant passage in which the second valve is installed may be larger than or equal to the inner diameter of the other refrigerant passage.

The compression unit is provided with one discharge port for discharging the refrigerant compressed in the compression unit in one direction with respect to the axial direction, and the compression unit is provided with a discharge cover for receiving the discharge port, And can be provided on the cover.

In order to achieve the object of the present invention, A compression unit disposed in an inner space of the casing and having a compression space for compressing the refrigerant and having a discharge port for guiding the refrigerant compressed in the compression space to the inner space of the casing; A discharge valve provided to open and close the discharge port according to a difference between an internal space pressure of the casing and a compression space pressure of the compression section; A discharge cover having a discharge space for receiving the discharge valve; A bypass pipe connecting between an inner space of the casing and a suction side of the compression section; A first hole communicating with the discharge space of the discharge cover, a second hole communicating with the internal space of the casing, and a third hole communicating with the bypass pipe, wherein the first hole and the second hole, A valve housing having a valve space communicated with all the holes; And a second hole communicating with the first position and the second position according to a difference between a pressure supplied through the first hole and a pressure supplied through the second hole, And a valve plate for selectively opening and closing the three holes of the high pressure type compressor.

Here, the valve housing may be fixedly coupled to the discharge cover inside the casing.

At least one of the first hole and the second hole is connected to the inside of the discharge cover by a connection pipe passing through the casing, and the valve housing is fixed to the center of the bypass pipe at the outside of the casing, Space or the internal space of the casing.

Here, a check valve may be further provided to prevent the refrigerant discharged from the internal space of the casing from flowing back into the internal space of the casing.

Further, in order to achieve the object of the present invention, A condenser connected to the compressor; A condenser fan provided at one side of the condenser; An evaporator connected to the condenser; And an evaporator fan provided at one side of the evaporator, wherein the compressor is provided with the high-pressure compressor as described above.

The high pressure type compressor according to the present invention and the refrigeration cycle apparatus using the same are provided with a check valve for preventing the refrigerant discharged from the compressor toward the condenser from flowing back to the compressor and a check valve between the internal space of the casing and the compression space By providing a bypass valve for eliminating the pressure difference, when the refrigerating cycle apparatus is stopped in a refrigerating cycle apparatus to which a high pressure type compressor such as a rotary compressor is applied, the suction side and the discharge side of the compressor can quickly assume a pneumatic state The compressor of the refrigeration cycle device can be restarted quickly.

In addition, it is possible to prevent damage to the overload preventing device and the motor, which may be caused when the restarting of the compressor is not smooth after the stop of the refrigeration cycle device, thereby improving the reliability of the compressor.

Further, since the bypass valve is a mechanical valve operated by a difference between the internal space pressure of the casing and the compression space pressure, the power consumption and the separate control unit for the bypass valve are not needed, It is possible to prevent a reduction in reliability due to a malfunction. In addition, the bypass valve can be installed inside the casing, thereby making it possible to miniaturize the compressor and to prevent it from being damaged during transportation.

In addition, it is possible to perform a so-called differential pressure operation in which the fan of the refrigeration cycle apparatus is operated for a period of time during which the compressor is stopped, thereby continuing the heat exchange, thereby enhancing the energy efficiency of the refrigeration cycle apparatus.

1 is a system diagram showing a refrigeration cycle apparatus according to the present invention.
FIG. 2 is a longitudinal sectional view showing a rotary compressor having an accumulator in the refrigeration cycle apparatus according to FIG. 1;
3 and 4 are a vertical sectional view and an exploded perspective view showing the first valve and the second valve, respectively, in the compressor according to FIG. 2,
Figures 5 and 6 are cross-sectional views assembled together with embodiments of the second valve according to Figure 4,
FIGS. 7A and 7B are sectional views showing the operation of the second valve according to the on / off state of the compressor in the second valve according to FIG. 4;
8A to 8C are schematic views for explaining the differential pressure operation, the pneumatic operation, and the restart operation in the refrigeration cycle apparatus according to FIG. 2;
FIGS. 9A and 10B are block diagrams showing operations of a conventional rotary compressor and a rotary compressor according to the present invention, and graphs showing changes in pressure and current, respectively. FIGS. 9A and 9B are views showing a conventional rotary compressor , Figures 10a and 10b are diagrams for the present invention,
11A and 11B are graphs showing a comparison between a refrigeration cycle apparatus to which the rotary compressor of the present invention is applied and a refrigeration cycle apparatus to which a conventional rotary compressor is applied. FIG. 11B is a graph showing a comparison between the restart timing and the stabilization step of the conventional rotary compressor and the rotary compressor of the present invention, and FIG.
FIGS. 12 to 14 are schematic views showing the installation of a second valve according to the type of the rotary compressor according to the present invention;
FIGS. 15 and 16 are schematic views showing other embodiments of the connecting position of the bypass pipe in the refrigeration cycle apparatus according to FIG. 2. FIG.

Hereinafter, a compressor according to the present invention, a refrigeration cycle apparatus using the same, and a method of operating the refrigeration cycle apparatus will be described in detail with reference to the accompanying drawings.

FIG. 1 is a system diagram showing a refrigeration cycle apparatus according to the present invention, and FIG. 2 is a longitudinal sectional view showing a rotary compressor having an accumulator in the refrigeration cycle apparatus according to FIG.

1, the refrigeration cycle apparatus according to the present embodiment includes a compressor 1, a condenser 2, an expansion valve 3, and an evaporator 4. When this refrigeration cycle apparatus is applied to a unitary air-conditioner, a compressor, an outdoor heat exchanger (condenser or evaporator), an outdoor fan (condenser fan or evaporator fan) and an expansion valve are installed in the outdoor unit, An indoor heat exchanger (evaporator or condenser) and an indoor fan (evaporator fan or condenser fan) are installed in the indoor unit.

Although not shown in the drawing, a refrigerant switching valve (not shown) is provided between the discharge side and the suction side of the compressor 1 to switch the circulation direction of the refrigerant discharged from the compressor 1 to the outdoor unit or the indoor unit, For cooling or heating. In Fig. 1, a refrigerant switching valve is shown as a system diagram, not shown, for cooling.

The high-pressure refrigerant discharged from the compressor 1 moves to a condenser 2 installed in the outdoor unit. The refrigerant is condensed in the condenser 2 and expanded while passing through the expansion valve 3. The expanded refrigerant is introduced into the indoor unit And then the refrigerant is sucked back into the compressor 1 while being evaporated through the evaporator 4 installed. Here, the compressor (1) can be constituted by a rotary compressor having a discharge pressure state in which the internal space of the casing is high pressure.

Referring to FIG. 2, the rotary compressor 1 according to the present embodiment is provided with an electric section in the inner space of the compressor casing 10, compresses the refrigerant under the transmission section 20, (Not shown) to the inner space 10a. The transmission portion (20) and the compression portion (30) are mechanically connected by the rotation shaft (23).

The rotor 20 is fixed to the compressor casing 10 by inserting the stator 21 into the compressor casing 10. The rotor 22 is rotatably inserted into the stator 21. The rotary shaft (23) is press-fitted to the center of the rotor (22).

The compression unit 30 is provided with a main bearing 31 for supporting the rotary shaft 23 and fixed to the inner circumferential surface of the compressor casing 10 and a rotary shaft 23 A main bearing 31 and a sub bearing 32 are provided between the main bearing 31 and the sub bearing 32 so as to form a compression space 33a, (33). The cylinder 33 is bolted to the main bearing 31 together with the sub-bearing 32 and fixed.

The compression chamber 33a of the cylinder 33 is provided with a rolling piston 34 which is coupled to the eccentric portion of the rotary shaft 23 and compresses the refrigerant while pivotally moving. On the inner wall of the cylinder 33, a rolling piston 34 And the vane 35 dividing the compression space 33a into the suction chamber and the compression chamber together with the rolling piston 34 is slidably inserted.

A first discharge port 31a for discharging the refrigerant compressed in the compression space 33a is formed in the main bearing 31. A first discharge port 31a for opening and closing the first discharge port 31a is formed at the end of the first discharge port 31a, A valve 36 is provided. A first discharge cover (37) having a first discharge space (37a) is provided on the upper surface of the main bearing (31).

The sub bearing 32 is provided with a second discharge port 32a for discharging the refrigerant compressed in the compression space 33a and a second discharge port 32a for opening and closing the first discharge port 32a is formed at the end of the second discharge port 32a. A valve 38 is provided. On the upper surface of the sub bearing 32, a first discharge cover 39 having a second discharge space 39a is provided.

The compression unit 30 is provided with a first discharge space 37a for discharging the refrigerant discharged to the second discharge space 39a or a space between the compression unit 30 and the transmission unit 20 A plurality of coolant passages 30a and 30b are formed. The more the refrigerant passage is possible, the faster the refrigerant discharged into the second discharge space 39a can be moved toward the discharge pipe 16. In the drawing, the first refrigerant passage 30a and the second refrigerant passage 30b are shown.

The first refrigerant passage 30a and the second refrigerant passage 30b are formed by axially penetrating the sub bearing 32, the cylinder 33, and the main bearing 31, respectively. The first refrigerant passage 30a may be formed to be accommodated in the inner space 37a of the first discharge cover 37 or may be formed to be exposed to the outside of the first discharge cover 37. [

However, the second refrigerant passage 30b is preferably exposed to the outside of the first discharge cover 30a, which may be advantageous for mounting the second valve 130, which will be described later. The second valve will be described later.

The inner diameter D1 of the first refrigerant passage 30a and the inner diameter D2 of the second refrigerant passage 30b may be formed identically. However, in some cases, the inner diameter D1 of the first refrigerant passage 30a and the inner diameter D2 of the second refrigerant passage 30b may be different from each other.

For example, the first refrigerant passage 30a is a passage for guiding the refrigerant discharged to the second discharge cover 39 to the first discharge cover 37 or the inner space 10a of the casing 10, When the second valve 130 to be described later is mounted on the second refrigerant passage 30b, the inner diameter D2 of the second refrigerant passage 30b is formed to be larger than the inner diameter D1 of the first refrigerant passage 30a It is possible to quickly move the second valve plate 132 to a second position (bypass pipe closing position) P2 to be described later by overcoming the weight of the second valve plate 132 to be described later at the time of restarting the compressor .

The first discharge valve 36 and the second discharge valve 38 are located at a position where the internal pressure Ps of the compression space 33a and the internal pressure of the internal space 10a of the compressor casing 10 , And discharge pressure) Pd. Therefore, when the suction pressure Ps is too low, the pressure difference between the suction pressure Ps and the discharge pressure Pd becomes too large, and the suction pressure Ps becomes equal to the discharge possible pressure The refrigerant in the compression space 33a can not be discharged. Then, the overload prevention device 50 provided in the power transmission portion 20 is operated by overloading the transmission portion 20 (hereinafter, mixed with the motor) 20 to stop the motor to remove the compression load from the compression portion 30 .

The compressor casing 10 includes a circular cylindrical body 11 having both upper and lower ends opened and an upper cap 12 and a lower cap 13 which cover upper and lower ends of the circular cylinder 11 to seal the inner space 10a, ≪ / RTI > A suction pipe 15 connected to the outlet side of the accumulator 40 to be described later is connected to the lower half of the circular cylinder 11 and a discharge side refrigerant pipe L1 is connected to the inlet side of a condenser 2, A discharge tube 16 connected to the discharge tube 16 can be coupled. The suction pipe 15 is directly connected to the suction port 33b of the cylinder 33 through the circular cylinder 11 and the discharge pipe 16 passes through the upper cap 12 and is connected to the inner space of the compressor casing 10 10a.

An accumulator 40 is disposed on one side of the compressor casing 10 and an internal space 40a separated from the internal space 10a of the compressor casing 10 is formed inside the accumulator 40 to have a predetermined volume . The accumulator 40 is connected to the upper portion of the evaporator 4 through a suction side refrigerant pipe L2 and the suction pipe 15 connected to the cylinder 33 of the compressor casing 10 is connected to the lower portion of the accumulator 40 have.

The suction side refrigerant pipe L2 is connected to the upper surface of the accumulator 40 and the suction pipe 15 is formed in the shape of an elongated L and penetrates the lower surface of the accumulator 40, ) Of the inner surface of the base plate 10 by a predetermined height.

The rotary compressor according to this embodiment operates as follows.

That is, when power is applied to the stator 21, the rotor 22 and the rotary shaft 23 rotate within the stator 21, and the rolling piston 34 performs a pivotal motion. The volume of the suction chamber is changed and the refrigerant is sucked into the cylinder 33.

The refrigerant is compressed and compressed in the compression space 33a by the rolling piston 34 and the vane 35 so that the first discharge port 31a provided in the main bearing 31 and the first discharge port 31b provided in the sub bearing 32 And is discharged to the first discharge cover 37 and the second discharge cover 39 through the second discharge port 32a.

The refrigerant discharged to the first discharge cover 37 is directly discharged to the inner space 10a of the casing 10 while a portion of the refrigerant discharged to the second discharge cover 39 is discharged to the first refrigerant passage 30a To the discharge space 37a of the first discharge cover 37 or to the inner space 10a of the casing 10. [ However, a part of the refrigerant discharged into the second discharge space 39a of the second discharge cover 39 is guided to the second valve 130 through the second refrigerant passage 30b so that the second valve plate 132 The bypass pipe 120 to be described later is cut off. This will be described later.

On the other hand, the refrigerant, which has moved to the inner space 10a of the casing 10 through the first refrigerant passage 30a, is discharged to the refrigerating cycle apparatus through the discharge pipe 16. The refrigerant discharged to the refrigerating cycle apparatus is discharged to the condenser The refrigerant flows into the accumulator 40 through the accumulator 40 before the refrigerant is sucked into the compression space 33a of the cylinder 33 and flows into the accumulator 40 through the expansion valve 3 and the evaporator 4, The oil is separated from the gas refrigerant so that the gas refrigerant is sucked into the compression space 33a of the cylinder 33 d while the liquid refrigerant is evaporated in the inner space 40a of the accumulator 40, And then sucked into the suction port 33a.

At this time, the condensing fan 2a and the evaporation fan 4a are operated to increase the temperature of the surrounding area in the condenser 2, while the conventional refrigeration cycle device that lowers the ambient temperature in the evaporator 4 continues to operate.

On the other hand, when the operation of the refrigerating cycle apparatus is stopped, the compressor 1 is also stopped, so that no more refrigerant is discharged toward the condenser in the compressor 1. However, the refrigerant discharged from the compressor 1 to the refrigeration cycle apparatus is discharged to the evaporator (not shown) which is relatively low in the condenser 2, which is relatively high in pressure due to the pressure difference between the suction side and the discharge side, 4) direction. Accordingly, when the condensing fan 2a and the evaporation fan 4a of the refrigerating cycle apparatus are operated even when the compressor 1 is stopped, that is, in a state where the compression load of the compression unit 30 is removed, The heat exchange in the condenser 2 and the evaporator 4 can be continued using the latent heat during the operation of the refrigeration cycle apparatus, thereby increasing the efficiency of the refrigeration cycle apparatus.

However, even when the pressure difference between the suction pressure (pressure in the compression space) Ps and the discharge pressure (pressure in the casing interior space) Pd is as small as 1 kgf / cm 2 due to the characteristics of the rotary compressor, The time required should be long. However, when the time required for the pressure control is long, the oil leakage increases, and therefore, the time required for the pressure control can not be prolonged. Therefore, it is necessary to keep the time required for the pressure reduction as short as possible. However, since the compressor 1 can not reach the pressure required for restarting, the compressor 1 can not restart even if the refrigeration cycle apparatus is operated again. However, if the time required for pneumatic pressure is shortened, the latent heat in the differential pressure section can not be sufficiently utilized, and energy efficiency may be lowered accordingly.

A check valve (hereinafter referred to as a first valve) 110 is provided at the inlet end or the inlet end of the discharge pipe 16 in the internal space 10a of the compressor casing 10, A bypass pipe 120 and a bypass for selectively opening and closing the bypass pipe 120 are provided between the inlet end of the first valve 110 and the suction side of the accumulator 40 based on the direction of discharge from the bypass pipe 1, By providing a valve (hereinafter referred to as a second valve) 130, it is possible to shorten the period of time during which the compressor is stopped and sufficiently utilize the latent heat, thereby improving the energy efficiency.

For convenience, a flow path connecting the discharge side and the suction side with reference to the compressed portion is referred to as a first refrigerant flow path (Q1), and a flow path for bypassing between both end portions of the first refrigerant flow path (Q1) (Q2). One end of the second refrigerant passage Q2 is connected to the discharge side on the basis of the compression section (more precisely, the discharge valve) 30 and the other end of the second refrigerant passage Q2 is connected to the suction side Can be connected.

One end of the first refrigerant passage Q1 is connected to the first discharge valve 36 of the compression section 30 and the second discharge valve 38 of the compressor casing 10, The first refrigerant flow path Q1 is configured such that the refrigerant discharged into the internal space 10a of the compressor casing 10 flows from the condenser 2 to the compression space 33a of the cylinder 33 on the suction side, (3) and an evaporator (4), and is connected to the compression space (33a).

The second refrigerant passage Q2 is connected to the inner space 10a of the compressor casing 10 and the compression portion 30a of the compressor casing 30 based on the first discharge valve 36 and the second discharge valve 38 of the compression portion 30. [ The evaporator 4 and the condenser 2, the expansion valve 3 and the evaporator 4 between the compression chambers 33a and 33a of the condenser 2 and the evaporator 4, respectively.

1 and 2, the second refrigerant passage Q2 is connected to the second valve 130 provided in the inner space 10a of the compressor casing 10 and the second valve 130 provided in the inner space 40a of the accumulator 40, And a bypass pipe 120 to which both ends are connected.

FIGS. 3 to 5 are longitudinal sectional views showing the first valve and the second valve, respectively, in the compressor according to FIG. 2;

1 and 2, the first valve 110 may be installed at the inlet end of the discharge pipe 16 in the inner space 10a of the compressor casing 10. [ This makes it possible to reduce the internal volume of the compressor 1 substantially as compared with the case where the first valve 110 is installed in the discharge pipe 16 from the outside of the casing 10, .

Here, the first valve 110 is provided in the first valve 110 when the refrigerant discharged from the compressor casing 10 toward the condenser 2 is stopped when the compressor 10 is stopped, that is, when the compression load is removed in the compression space 33a Way valve capable of blocking the backflow into the internal space 10a of the valve 10a. Of course, the first valve 110 may be an electronic valve, but a mechanical valve may be suitable considering cost and reliability.

3, the first valve 110 includes a first valve housing 111 connected to an inlet end or an inlet end of the discharge pipe 16 in the internal space 10a of the compressor casing 10, And a first valve plate 112 which is accommodated in the first valve space 115c of the first valve housing 111 and opens and closes the first valve housing 111 while moving in accordance with the pressure difference between both sides.

The first valve housing 111 may be formed as a single body. However, since the first valve plate 112 is inserted into the first valve space 111a, the first valve housing 111 is assembled with the first housing body 115 and the first valve cover 116, It is preferable to form the valve space 111a.

The first housing main body 115 is opened at its both ends to form a condenser side opening end (first opening end) 115a and a compressor side opening end (second opening end) 115b. Accordingly, a first valve space 111a through which the first valve plate 112 can move is formed between the first opening end 115a and the second opening end 115b.

The discharge pipe 16 is connected to the first opening end 115a of the first housing main body 115 and the first valve cover 116 is inserted into the second opening end 115b. The first valve cover 116 has a plurality of through holes 116a formed in an arc shape so as to be opened and closed by the first valve plate 112. [

Although the first valve plate 112 may be formed in a piston shape, the first valve plate 112 opens and closes the through-hole 116a of the first valve cover 116 to one side thereof, May be preferable in consideration of the valve responsiveness and the like.

The first valve plate 112 is formed with a gas communication groove 112a at the center thereof. When the first valve plate 112 is in contact with the first opening end 115a, the first opening end 115a is opened while the first valve plate 112 is in the second opening end 115b. The through hole 116a of the second valve cover 116 provided at the second opening end 115b is completely blocked.

As described above, a bypass pipe 120 is connected between the second discharge cover 39 and the accumulator 40, and a second valve (also referred to as a check valve) 130 are installed.

When the compressor 1 is stopped and the compression load of the compression space 33a is removed, the second valve 130 is simultaneously opened while the compressor is stopped, and the compressor 1 is restarted so that the compression space 33a The second valve 130 is closed at the same time when the compressor 1 is restarted.

4 and 5, the second valve 130 according to the present embodiment includes a second valve housing 131 having a second valve space 131a, a second valve housing 131, And a second valve plate 132 which is inserted into the valve space 131a of the bypass pipe 131 and selectively opens and closes the bypass pipe 120.

The second valve housing 131 may be formed as a single body. However, since the second valve plate 132 is inserted into the second valve space 131a, the second valve housing 131 is formed in the same manner as the first valve housing 111, It is preferable that the cover 136 is assembled to form the second valve space 131a.

A second valve space 131a is formed in the second housing main body 135 so that the second valve plate 132 can move in accordance with a pressure difference. Accordingly, the second valve space 131a is formed to have a length such that the second valve plate 132 moves in the longitudinal direction and the third hole 136a, which will be described later, can be opened and closed.

A high pressure side hole (hereinafter referred to as a first hole) 135a communicating with the second refrigerant passage 30b of the compression section 30 is formed at one side of the second housing main body 135, (Hereinafter referred to as a second hole) 136a communicating with the inner space of the casing 10 and a bypass side communicating with the bypass pipe 120 is formed on the side surface of the second housing main body 135 (Hereinafter referred to as a third hole) 135b. That is, the first hole 135a, the second hole 136a, and the third hole 135b are both formed to communicate with the second valve space 131a.

The inner surface of the second housing body 135 on the side where the first hole 135a communicates may be inclined so as to be narrowed toward the first hole. When the second valve plate 132 is moved to the first position (P1) which is the first hole 135a side and the areas of both sides of the second valve plate 132 exposed to the refrigerant are compared (Hereinafter referred to as a first surface) 132a facing the first hole 135a in the first position P1 is an upper surface (hereinafter referred to as a second surface) (hereinafter referred to as a second surface) So that the refrigerant supplied through the first hole 135a can press the entire first surface 132a of the second valve plate 132 when the compressor is restarted The second valve plate 132 can quickly move toward the second hole 136a even if the second valve plate 132 receives the discharge pressure of the space inside the casing on the second surface.

The distance between the first hole 135a and the second hole 136a is set such that the second valve plate 132 is moved in the first position P1 and the second position 136 in the longitudinal direction of the second valve housing 131 P2 so that the third hole 135b can be opened and closed.

The cross-sectional area of the first hole 135a may be the same as the cross-sectional area of the second hole 136a. However, in order for the second valve plate 132 to quickly open the bypass pipe when the compressor is stopped, Sectional area of the first hole 135a may be larger than the cross-sectional area of the first hole 135a. For example, when the cross-sectional area of the first hole 135a is larger than the cross-sectional area of the second hole 136a, even when the compressor is stopped, the second valve plate 132 facing the first hole 135a The first surface 132a may be subjected to a higher pressure than the second surface 132b of the second valve plate 132 facing the second hole 136a. Then, the descending speed of the second valve plate 132 is delayed, so that the third hole 135b communicated with the bypass pipe can not be opened quickly.

Therefore, it is preferable that the cross-sectional area of the second hole 136a is formed larger than the cross-sectional area of the first hole 135a in order to allow the second valve plate 132 to be opened quickly when the compressor is stopped. In order to allow the second valve plate 132 to open more quickly when the compressor is stopped as shown in FIG. 6, a compression coil having a predetermined elastic force is provided between the second valve plate 132 and the second valve cover 136, An elastic member 133 such as a spring may be further provided.

The third hole 135b is formed in the main wall surface of the second housing main body 135 so as to intersect the center line of the first hole 135a or the second hole 136a and the third hole 135b Is formed to be smaller than or equal to the thickness of the second valve plate 132 in the moving direction. 7A, when the second valve plate 132 reaches the first position P1 at which the first hole 135a is blocked, the third hole 135b is opened, and as shown in FIG. 7B The third hole 135b is closed by the side surface of the second valve plate 132 when the second valve plate 132 reaches the second position P2 at which the second hole 136a is blocked, The third hole 135b is formed to close together at the position where the second hole 136a is closed by the side surface 132c of the second valve plate 132. [

The inner diameter D3 of the bypass pipe 120 may be equal to or smaller than the inner diameter of the discharge pipe 16 or the discharge side refrigerant pipe L1 or the inner diameter D4 of the suction side refrigerant pipe L2. When the inner diameter D3 of the bypass pipe 120 is larger than the inner diameter D4 of the discharge pipe 16 or the discharge side refrigerant pipe or the inner side refrigerant pipe L2 of the suction side refrigerant pipe L2, The cost of the second valve 130 can be increased because the size of the second valve 130 must be increased.

The refrigeration cycle apparatus including the rotary compressor according to the present embodiment as described above operates as follows. Figs. 8A to 8C are schematic views showing the differential pressure operation, the pneumatic operation, and the restart operation in the refrigeration cycle apparatus according to Fig. 2, respectively.

Referring to FIG. 8A, when the compressor stops, the refrigerant discharged from the internal space 10a of the compressor casing 10 through the discharge pipe 16 toward the condenser flows back into the internal space 10a of the compressor casing 10, But this can be suppressed by the first valve 110. [ Accordingly, the refrigerant can move only in the direction of the accumulator 40 from the condenser 2 through the expansion valve 3 and the evaporator 4 according to the pressure difference. At this time, if the condenser fan 2a or the evaporator fan 4a is operated, the refrigerant passing through the condenser 2 and the evaporator 4 can be heat-exchanged with the air even when the compressor 1 is stopped, Can be improved.

8B, the compressor 1 is stopped and the second valve 130 is opened to open the bypass pipe 120 as shown in FIG. 8A. That is, when the compressor 1 is stopped, the second valve 130 does not discharge the refrigerant from the compression space 131a to the second discharge space 39a of the second discharge cover 39.

7A, the refrigerant remaining in the second discharge space 39a of the second discharge cover 39 is discharged to the first refrigerant passage 30a in accordance with the pressure difference with the inner space 10a of the casing 10, To the first discharge space (or the inner space of the casing) 37a. A part of the refrigerant remaining in the second discharge space 39a of the second discharge cover 39 is discharged through the second refrigerant passage 30b to the first discharge port 39a of the second valve housing 131 close to the first hole 135a of the second valve housing 131 The pressure of the refrigerant moving to the first hole 135a is lowered so that the second valve plate 132 can not be pushed up, The first hole 135a is lowered by its own weight (or the restoring force of the valve spring) and the internal pressure of the casing 10 flowing through the second hole 136a, And the bypass pipe 120 is opened.

Some of the refrigerant discharged from the compressor casing 10 does not move in the direction of the condenser and the refrigerant flows between the pressure of the inner space 10a of the compressor casing 10 and the pressure of the inner space 40a of the accumulator 40 And moves toward the bypass pipe 120 by the difference to move to the internal space 40a of the accumulator 40. [ The pressure of the internal space 40a of the accumulator 40 and the pressure of the internal space 10a of the compressor casing 10 form a pneumatic pressure within a predetermined range (usually, 1 kgf / cm2 or less).

Then, the compressor 1 keeps the suction pressure Ps and the discharge pressure Pd in a pressure-pressure state in which the compressor can start, and the compressor 1 can wait for restarting. Accordingly, the internal pressure of the compressor casing is further lowered, and the first valve is quickly closed (CLOSE), so that the refrigerant discharged toward the condenser can be prevented from flowing back to the compressor.

Next, referring to FIG. 8C, when the user selects the re-operation for the instantly stopped refrigeration cycle apparatus, as the suction pressure Ps and the discharge pressure Pd are brought into the pneumatic state as seen in 8b, (1) is quickly restarted. The refrigerant compressed in the compression space 33a is discharged to each of the first discharge cover 37 and the second discharge cover 39 while pushing the first discharge valve 36 and the second discharge valve 38 together. 7B, a part of the refrigerant discharged into the second discharge space 39a of the second discharge cover 39 flows into the first hole 135a of the second valve housing 131 through the second refrigerant passage 30b . The refrigerant moving to the first hole 135a is in a state of a high pressure relative to the internal pressure of the casing 10 so that the second valve plate 132 is pushed in the direction of the second hole And the second valve plate 132 moves to the second position P2 close to the second hole 136a to block the second hole 136a and the third hole 135b together.

Then, the bypass tube 120 is closed so that the refrigerant discharged into the internal space 10a of the compressor casing 10 is prevented from bypassing in the accumulator direction, so that the internal pressure of the compressor casing 10 is increased.

The first valve 110 is opened according to the pressure difference between the internal pressure of the casing 10 and the inlet side of the condenser 2 so that the refrigerant discharged into the internal space of the compressor casing 10 Is discharged in the direction of the condenser through the discharge pipe 16 so that the refrigerating cycle apparatus can be smoothly re-operated.

FIGS. 9A and 10B are block diagrams showing operations of a conventional rotary compressor and a rotary compressor according to the present invention, and graphs showing a pressure change and a current change therebetween. FIGS. 9A and 9B are views showing a conventional rotary compressor , Figs. 10A and 10B are views showing the present invention.

Referring to FIG. 9A, when the conventional rotary compressor is applied to the refrigeration cycle apparatus, the discharge pressure Pd is continuously lowered and the suction pressure Ps temporarily rises when the compressor stops.

Here, when the user operates the refrigeration cycle apparatus and power is applied to the compressor, the pressure difference within the compressor, that is, the differential pressure [ Delta] P between the suction pressure Ps and the discharge pressure Pd, / Cm < 2 >), the compressor immediately resumes operation.

However, if the pressure difference inside the compressor is greater than the pre-pressure condition, the compressor will not start and will not compress or discharge the refrigerant gas. Then, an overcurrent is generated in the drive motor, which is the electric motor, and the overload prevention device 50 operates to cut off the power supplied to the drive motor. Then, after the return time of the overload protection device 50, the overload protection device 50 is returned and the power is again applied to the driving motor. However, if the pressure inside the compressor still does not satisfy the pneumatic condition, the above operation is repeated. As described above, since the conventional rotary compressor takes a long time to reach the pneumatic condition, this process is repeated several times.

This graph is shown in FIG. 9B. That is, when the compressor is stopped, the refrigerant discharged from the compressor 1 flows into the compressor through both of the refrigerant cycle leading to the condenser 2, the expansion valve 3 and the evaporator 4, so that the discharge pressure (solid line) . Experimental results show that it takes about 20 minutes to reach the pressure condition (compressor pressure condition) in which the compressor can restart.

Then, until the pneumatic condition is reached, the driving motor is supplied with the restarting current as shown in the lower graph of FIG. 9B. However, as the compressor fails to restart several times, the current shows a high peak point periodically. The point at which this peak point appears is the point where the overload protection device 50 operates, and the interval between these peak points is the period when the overload protection device 50 returns again. As shown in the figure, the peak points gradually move away from each other because the overload prevention device 50 is overheated as the compressor repeatedly fails to restart. Therefore, it is known that the overload preventing device 50 is repeatedly operated to prevent the overload of the motor due to the continuous application of the current to the drive motor even though the compressor is not able to reach the rest pressure condition. .

On the other hand, referring to FIG. 10A, even when the rotary compressor of the present embodiment is applied to the refrigeration cycle apparatus, the discharge pressure temporarily decreases and the suction pressure temporarily rises when the compressor stops. Thereafter, when the discharge pressure rises and the suction pressure decreases and the pressure difference becomes a predetermined range or more, the second valve 130 is switched to the open state in accordance with the pressure difference.

A part of the refrigerant remaining in the inner space 10a of the compressor casing 10 moves to the suction side which is the low pressure portion through the bypass pipe 120 so that the suction pressure inside the compressor Ps and the discharge pressure Pd satisfy the conditions of the pneumatic pressure quickly.

At this time, when the user operates the refrigeration cycle apparatus and power is applied to the driving section 20 of the compressor, the pressure difference inside the compressor has already met the pressure condition (normally, within 1 kgf / cm 2) Resume. Of course, the compressor may not be able to restart at one time for other reasons, but there is much less restart failure than with conventional rotary compressors. This can be confirmed also in FIG. 10B. FIG. 10B is a graph showing an experiment in which the compressor is restarted by repeatedly turning on / off the refrigeration cycle device for several times as shown in FIG. 9B.

As shown, the discharge pressure (bold solid line) at the time of stopping the compressor is momentarily lowered, and the suction pressure temporarily rises and remains constant.

At this time, the second valve 130 operates to open the bypass pipe 120, and a part of the refrigerant discharged to the inner space 10a of the compressor casing 10 based on the compression unit is discharged through the bypass pipe 120, The discharge pressure Pd and the suction pressure Ps within the compressor quickly reach the pneumatic condition while moving to the inner space 40a of the compressor 40. As a result, A solid line) is formed.

Accordingly, as shown by a bold solid line in Fig. 10B, it can be seen that the compressor of the present invention performs several times of restarting for the same period of time as compared with Fig. 9B while the discharge pressure Pd is repeated several times.

As shown in the lower part of FIG. 10B, when the restarting current is supplied to the motor, it can be seen that the normal current supply is performed in most sections at the time of restarting and the operation is restarted stably.

In this way, when the refrigeration cycle apparatus is stopped, the compressor is stopped, and the suction pressure and the discharge pressure can be quickly set to the normal pressure, so that the compressor can be restarted smoothly. As a result, the overload- It is possible to prevent the failure of the overload protection device from occurring in advance. In addition, the over-heating of the drive motor due to over-compression prevents burn-out of the drive motor, thereby improving the reliability of the compressor.

In addition, even if the refrigeration cycle apparatus to which the high-pressure compressor such as the rotary compressor is temporarily stopped, the so-called differential pressure operation in which the fan of the refrigeration cycle apparatus is operated for the stopped time can be continued to improve the energy efficiency of the refrigeration cycle apparatus have. This can be seen from Figs. 11A and 11B. FIG. 11A is a graph showing a relative comparison of latent heat periods when the conventional rotary compressor and the rotary compressor of the present invention are stopped during operation under the same load, FIG. 11B is a graph showing a comparison between the conventional rotary compressor and the restart timing And a stabilization step.

Referring to FIG. 11A, it can be seen that the suction pressure suddenly increases at the time when the compressor is stopped and gradually increases thereafter, but in particular, the conventional case increases rapidly from a higher pressure than the case of the present invention. On the other hand, it can be seen that the discharge pressure suddenly decreases at the point of time when the compressor is stopped and gradually decreases thereafter, but in particular, the conventional case rapidly decreases at lower pressure than the case of the present invention.

This is because a part of the refrigerant discharged from the compressor in the related art is backwardly flowed toward the compressor which is relatively low in pressure by the pressure difference at the time of stop of the compressor and the refrigerant flowing backward is relatively higher in pressure than the refrigerant left in the inner space of the compressor casing . Then, the refrigerant remaining in the inner space of the compressor casing is pushed out, and the pushed refrigerant leaks toward the accumulator through the gap between the members constituting the compression section. Accordingly, the suction pressure of the conventional rotary compressor increases sharply while the discharge pressure decreases sharply as a part of the refrigerant flows back toward the compressor.

On the other hand, in the case of the present invention, the first valve 110, which is a check valve, is installed in the discharge pipe so as to prevent the refrigerant from flowing back to the compressor from the condenser side. Thus, the suction pressure is low and the discharge pressure is high State can be maintained. In addition, as the variation range of the suction pressure and the discharge pressure is relatively low, the latent heat utilization rate in the same section is increased by about 35%. This is a shaded region in FIG. 11A.

Therefore, in view of the heat exchange efficiency in the unitary type refrigeration cycle apparatus, the size of the heat exchangeable section and the pressure difference in the state where the compressor is stopped, the energy efficiency is improved while the power consumption is reduced while the present invention is improved do.

In addition, in the conventional case, the refrigerant leaks toward the accumulator in the compressor casing, and the oil remaining in the compressor casing is pushed out together with the oil. Therefore, oil shortage may occur in the internal space of the compressor casing, The frictional loss can be increased, but the present invention can also reduce the friction loss due to this reason, thereby further enhancing the energy efficiency.

Referring to FIG. 11B, when the conventional rotary compressor is applied, the refrigerant discharged from the compressor circulates through the condenser, the expansion valve, and the evaporator as described above. Therefore, the compressor can be restarted, The time required for satisfying the pneumatic pressure condition (differential pressure: within 1 kgf / cm 2) (the time required for pneumatic pressure) is much larger than in the present invention. Accordingly, the restartable point of time of the conventional rotary compressor becomes considerably slower than the restartable point of time of the rotary compressor of the present invention. Accordingly, when the user uses the conventional rotary compressor, the compressor is not quickly restarted even if the refrigeration cycle device is tried to be operated again. As a result, the refrigeration cycle device can not resume operation rapidly. And the like.

In contrast, according to the present invention, since the pressure is preliminarily applied using the bypass pipe 120 and the second valve 130 at the same time as the compressor is stopped as described above, a separate time required for pneumatic pressure is unnecessary, . Accordingly, when the user desires to restart the refrigeration cycle apparatus, the compressor is rapidly restarted, and the refrigeration cycle apparatus can enter normal operation much faster than the conventional system. Therefore, the present invention can be significantly improved in energy efficiency as compared with the prior art.

In addition, it can be seen that the present invention enters the stabilization stage much faster than the prior art even when the stable load section of the refrigeration cycle apparatus is viewed. Accordingly, it can be seen that the refrigeration cycle apparatus to which the rotary compressor of the present invention is applied can be improved in energy efficiency as compared with the refrigeration cycle apparatus to which the conventional rotary compressor is applied.

Also, since the second valve constituting the bypass valve is constituted by the mechanical valve operated by the difference between the internal space pressure of the casing and the compression space pressure as in the present invention, the power consumption for the second valve, It is possible to reduce the manufacturing cost and to prevent the reliability from being deteriorated due to the malfunction. In addition, the second valve can be installed inside the casing, thereby making it possible to miniaturize the compressor and prevent the second valve from being damaged during transportation.

Meanwhile, another embodiment of the rotary compressor according to the present invention is as follows.

That is, in the above-described embodiment, when the compressor is discharged in both directions, the second valve is installed in any one of the plurality of refrigerant passages. However, in the present embodiment, even when the compressor is discharged in one direction, the same second valve as in the above embodiment can be applied.

For example, when the discharge port 31a is formed only on the main bearing 31, the second valve 130 provided on the main bearing 31 may be provided on the discharge cover 37 as shown in FIG. Thereby, the first hole 135a of the second valve 130 communicates with the discharge space 37a of the discharge cover 37. At this time, the second valve housing 131 of the second valve 130 may be installed to be in contact with the discharge cover 37. The second valve housing 131 is fixed to the inner circumferential surface of the casing 10 and is connected to the first hole 135a of the second valve housing 131 and the discharge space 37a of the discharge cover 37 by a separate connecting pipe. .

In this case, since the discharge space 37a of the discharge cover 37 is positioned adjacent to the internal space 10a of the casing 10, the internal pressure of the discharge cover 37 and the internal pressure of the casing 10 May not be large. Therefore, in order to secure a pressure difference between the internal pressure of the discharge cover 37 and the internal pressure of the casing 10, a discharge opening (not shown) of the discharge cover 37 communicating with the internal space 10a of the casing 10 Or the sectional area of the second hole 136a may be longer than the sectional area of the first hole 135a.

The basic configuration and operation effects of the compressor according to the present embodiment as described above, or the basic structure and operation effects of the refrigeration cycle apparatus including the compressor, are the same as those of the above-described embodiments, and thus a detailed description thereof will be omitted.

Meanwhile, another embodiment of the rotary compressor according to the present invention is as follows.

That is, in the above-described embodiment, the second valve is provided in the inner space of the casing. However, the second valve may be provided outside the casing.

13, when the second valve 130 is installed outside the casing 10, the third hole 135b of the second valve housing 131 is bypassed from the outside of the casing 10, The first hole 135a and the second hole 136a are connected to the pipe 120 by the connection pipes 141 and 142 passing through the casing 10 and the second discharge cover 37 The second discharge space 37a of the casing 10 and the inner space 10a of the casing 10. [ Of course, either one of the first hole 135a or the second hole 136a may be communicated to the discharge space of the discharge cover or the inner space of the casing without a separate connection pipe.

The basic configuration and operation effects of the compressor according to the present embodiment as described above, or the basic structure and operation effects of the refrigeration cycle apparatus including the compressor, are the same as those of the above-described embodiments, and thus a detailed description thereof will be omitted. However, in the case of the present embodiment, since the second valve is provided outside the casing, it may be advantageous for maintenance of the second valve.

Meanwhile, another embodiment of the rotary compressor according to the present invention is as follows.

That is, in the above-described embodiment, in the mouth type rotary compressor in which the casing is perpendicular to the paper surface, the second valve coincides with the axial direction of the rotary compressor. However, the casing may be installed horizontally or serially. Also in this case, it is preferable that the second valve is installed perpendicularly to the ground.

For example, when the casing 10 is installed horizontally as shown in FIG. 14, the second valve 130 may be installed in a direction perpendicular to the axial direction of the rotary shaft 23. This is because the second valve 130 of the present embodiment is operated using the pressure difference between the internal pressure of the casing 10 and the internal pressure of the second discharge cover 39 and the weight of the second valve plate 132 Because. However, when the valve spring 133 is mounted on the second valve 130 so that the second valve plate 132 is used together with the elastic force of the valve spring in addition to the differential pressure described above, It need not be arranged in a direction perpendicular to the paper surface.

The basic configuration and operation effects of the compressor according to the present embodiment as described above, or the basic structure and operation effects of the refrigeration cycle apparatus including the compressor, are the same as those of the above-described embodiments, and thus a detailed description thereof will be omitted. However, in the present embodiment, the installation type of the compressor is varied according to conditions, and the compressor is quickly pumped when the compressor is stopped, thereby preventing the restart from being delayed, and the energy efficiency can be increased by operating the refrigeration cycle even when the compressor is stopped.

Meanwhile, in the rotary compressor according to the present invention, the installation position of the first valve can be variously modified.

That is, in the above-described embodiment, the first valve is installed in the discharge pipe in the internal space of the casing. However, the first valve may be provided outside the compressor casing 10.

Even when the first valve 110 is installed outside the compressor casing 10 as described above, the basic configuration and operation effects are similar to those of the above-described embodiment, and thus a detailed description thereof will be omitted. However, in this case, since the first valve 110 is installed outside the casing 10, the maintenance of the first valve 110 may be advantageous.

15, the first valve 110 may be installed in the suction side refrigerant pipe L2 connected to the inlet end of the accumulator 40. [ In this case, it is possible to prevent the first valve 110 from being opened even if the second valve 130 is kept closed when the compressor 1 is stopped.

In the meantime, in the rotary compressor according to the present invention, there is another embodiment regarding the position where the bypass pipe is branched.

That is, in the above-described embodiment, the outlet end of the bypass pipe communicates with the internal space of the accumulator. However, in this embodiment, the outlet end of the bypass pipe 120 is connected to the suction pipe 15 .

In this case, as the internal space 10a of the casing 10 is directly communicated with the suction pipe 15, the time required for the pneumatic pressure can be further reduced. Since the oil or the liquid refrigerant discharged into the internal space 10a of the casing 10 can directly flow into the compression space 33a without passing through the internal space 40a of the accumulator 40, An oil separator or a liquid refrigerant separator 125 may be provided at an inlet end of the oil separator.

Meanwhile, in the above-described embodiment, the rotary compressor is applied only to the case of a single operation mode in which only a power operation including stoppage is performed. However, in some cases, a plurality The same can be applied to the case of the operation mode.

For example, if the power operation is a state in which a compressor is driven and a pressure load is generated, and a stop is a state in which a compressor is turned off (OFF) and a pressure load is removed, idling operation is performed, It can be said that the load is removed.

Therefore, if the first valve, the bypass pipe, and the second valve described in the above-described embodiments are applied, the idle operation can be performed between the suction side and the discharge side of the compression unit, if necessary.

Claims (17)

A casing having a closed inner space;
A driving motor provided in an inner space of the casing;
A compression unit disposed in an inner space of the casing and having a compression space for compressing the refrigerant and having a discharge port for guiding the refrigerant compressed in the compression space to the inner space of the casing;
A discharge valve provided to selectively open and close the discharge port according to a difference between an internal space pressure of the casing and a compression space pressure of the compression unit;
A first valve for preventing the refrigerant discharged from the internal space of the casing from flowing back to the internal space of the casing;
A bypass pipe connecting between an inner space of the casing and a suction side of the compression section; And
And a second pipe connected to the bypass pipe in the casing and selectively opening and closing the bypass pipe while moving between a first position and a second position in accordance with a difference between an internal pressure of the casing and a discharge- And a valve. The method according to claim 1,
Wherein the second valve closes the bypass pipe when a compression load is generated in the compression unit, and opens the bypass pipe when a compression load is removed from the compression unit. The method according to claim 1,
Wherein the second valve comprises:
Wherein a first hole communicating with the discharge side of the compression section is formed at one side of the valve space and a second hole communicating with the internal space of the casing is formed at the other side of the valve space, A valve housing in which a third hole communicating with the bypass pipe is formed between the hole and the second hole; And
And a valve plate inserted in the valve space of the valve housing and moving between the first position and the second position according to a difference between a pressure supplied to the first hole and a pressure supplied to the second hole, compressor. The method of claim 3,
Sectional area of the second hole is greater than or equal to a cross-sectional area of the first hole. The method of claim 3,
The third hole is formed in a direction crossing the center line of the first hole or the second hole,
And the inner diameter of the third hole is formed to be smaller than or equal to the thickness of the valve plate in the moving direction. The method of claim 3,
And the third hole is formed to be closed together by the valve plate at a position where the second hole is closed. The method of claim 3,
Wherein a valve spring is provided at one side of the valve plate to provide an elastic force to the valve plate. 8. The method of claim 7,
And the valve spring is provided at the second hole side with the valve plate interposed therebetween. The method according to claim 1,
And the second valve is installed between the drive motor and the compression unit. 10. The method of claim 9,
Wherein the discharge port is provided with a plurality of discharge ports so that the refrigerant compressed in the compression section is discharged in both directions with respect to the axial direction with reference to the compressed section,
A plurality of refrigerant passages are formed in the compression section such that the refrigerant discharged from one of the plurality of discharge ports is combined with the refrigerant discharged from the other discharge port,
And the second valve is installed so as to communicate with any one of the plurality of refrigerant channels. 11. The method of claim 10,
Wherein an inner diameter of the refrigerant passage in which the second valve is provided is formed to be equal to or larger than an inner diameter of the other refrigerant passage among the plurality of refrigerant passages. 10. The method of claim 9,
Wherein the compression unit is provided with one discharge port through which the refrigerant compressed in the compression unit is discharged in one direction with respect to the axial direction,
Wherein the compression unit is provided with a discharge cover for accommodating the discharge port,
And the second valve is provided in the discharge cover. A casing having a closed inner space;
A compression unit disposed in an inner space of the casing and having a compression space for compressing the refrigerant and having a discharge port for guiding the refrigerant compressed in the compression space to the inner space of the casing;
A discharge valve provided to open and close the discharge port according to a difference between an internal space pressure of the casing and a compression space pressure of the compression section;
A discharge cover having a discharge space for receiving the discharge valve;
A bypass pipe connecting between an inner space of the casing and a suction side of the compression section;
A first hole communicating with the discharge space of the discharge cover, a second hole communicating with the internal space of the casing, and a third hole communicating with the bypass pipe, wherein the first hole and the second hole, A valve housing having a valve space communicated with all the holes; And
And a second hole communicating with the first position and the second position in accordance with a difference between a pressure supplied through the first hole and a pressure supplied through the second hole, And a valve plate for selectively opening and closing the hole. 14. The method of claim 13,
And the valve housing is fixedly coupled to the discharge cover inside the casing. 14. The method of claim 13,
Wherein the valve housing is fixedly coupled to the center of the bypass tube outside the casing,
Wherein at least one of the first hole and the second hole communicates with an inner space of the discharge cover or an inner space of the casing by a coupling pipe passing through the casing. 14. The method of claim 13,
Further comprising a check valve for preventing the refrigerant discharged from the internal space of the casing from flowing back into the internal space of the casing. compressor;
A condenser connected to the compressor;
A condenser fan provided at one side of the condenser;
An evaporator connected to the condenser; And
And an evaporator fan installed at one side of the evaporator,
The compressor includes:
A refrigeration cycle apparatus comprising the high-pressure compressor according to any one of claims 1 to 16.

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