KR102403950B1 - High pressure compressor and refrigerating machine having the same - Google Patents

Abstract

The present invention is provided in the inner space of the casing, the compression space for compressing the refrigerant is provided, the compression unit is 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 the pressure of the inner space of the casing and the pressure of the compression space of the compression unit; a first valve for suppressing a reverse flow of the refrigerant discharged from the inner space of the casing into the inner space of the casing; a bypass pipe connecting the inner space of the casing and the suction side of the compression unit; And connected to the bypass pipe in the inside of the casing, selectively opening and closing the bypass pipe while moving between the first position and the second position according to the difference between the internal pressure of the casing and the pressure on the discharge side of the compression unit A high-pressure compressor including two valves and a refrigeration cycle device to which the same is applied may be provided.

Description

High-pressure compressor and refrigeration cycle device having the same

The present invention relates to a compressor, and more particularly, to a high-pressure compressor in which the inner space of a casing constitutes a high-pressure part, and a refrigeration cycle device having the same.

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

The compressor may be divided into an indirect suction method and a direct suction method according to a method of sucking the refrigerant into the compression chamber. In the indirect suction method, the refrigerant circulating in the refrigeration cycle is introduced into the inner space of the compressor casing and then sucked into the compression chamber. In the direct suction method, unlike the indirect suction method, the refrigerant is directly sucked into the compression chamber. The indirect suction method is classified as a low-pressure compressor, and the direct suction method is classified as a high-pressure compressor.

In the low-pressure 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, and accordingly, a separate accumulator is not provided. On the other hand, in the high-pressure compressor, an accumulator is generally provided on the suction side rather than the compression chamber in order to prevent liquid refrigerant or oil from flowing into the compression chamber.

In such a high-pressure compressor, the inner space of the casing constitutes a high-pressure part that is a discharge space, and the internal space of the accumulator constitutes a low-pressure part. 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 is large, so that the compressor cannot be instantly restarted. Therefore, in the air conditioners using most high-pressure compressors, after the operation of the compressor is stopped (OFF), the operation is stopped for a certain period of time to secure a flat pressure time to adjust the suction pressure and the discharge pressure within a certain range. It is carrying out an additional operation called '3 minute restart'.

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

However, if the time for the differential pressure of the refrigeration cycle device to reach the flat pressure (hereinafter, the differential pressure section or the time required for flat pressure) becomes longer, the oil in the compressor flows out through the gap between the members and the oil level is lowered, and the compressor is not restarted. However, there is a problem in that it is difficult to apply the high-pressure compressor to a refrigeration system such as an air conditioner. That is, by the difference between the suction pressure and the discharge pressure, the oil in the inner space of the casing flows out to the accumulator at a relatively low pressure compared to the inner space of the casing through the gap between the members and is stored in the inner space of the compressor casing. is lowered. In particular, the rotary compressor is not restarted even when the differential pressure between the suction pressure and the discharge pressure is as small as 1 kgf/cm 2 due to its characteristics. Therefore, once the compressor is stopped, the compressor is not easily restarted. However, if the input power is continuously supplied even in a state in which the compressor is not restarted due to the differential pressure, an overload occurs in the motor, and eventually, an overload protection device (OLP) is operated and the stop state of the compressor may be prolonged. Therefore, considering the oil leakage, the time for the compressor to reach the equilibrium pressure cannot be extended long, and accordingly, a rotary compressor with a short allowable period of equilibrium pressure is difficult to be applied to a refrigeration cycle device that uses latent heat for the period required for plateau pressure. Accordingly, there is a problem in that it is difficult to apply a rotary compressor, which is a high-pressure compressor, to an air conditioner in an area where the efficiency of the refrigeration cycle device is important.

Instead, in a unitary air conditioner to which a high-pressure compressor is applied, a method of installing an orifice between the condenser and the evaporator so that the differential pressure can be quickly reached from the flat pressure may be applied. However, if the time required for flat pressure is reduced by using an orifice, it is also impossible to use the latent heat of the differential pressure section, which is also disadvantageous in terms of efficiency. there was.

In addition, when the conventional rotary compressor is applied, the overload prevention device for preventing overload of the motor is repeatedly operated as the restart of the compressor is not smoothly performed during re-operation after stopping the refrigeration cycle. As the protection device is damaged or burnt out due to overheating of the motor, there is also a problem in that the reliability of the compressor is deteriorated.

In addition, in consideration of these problems, a bypass pipe is connected between the discharge side and the suction side of the compressor, and a solenoid valve is installed in the middle of the bypass pipe. It may be possible to achieve even pressure. However, in this case, not only separate power is required to operate the solenoid valve, but also a separate control unit is required to selectively operate the solenoid valve, which increases manufacturing cost and is concerned about reliability degradation due to malfunction. There was a problem. In addition, since the solenoid valve is weak to high temperature and has a limitation in installing it inside the casing of the compressor, it is usually installed outside the casing.

SUMMARY OF THE INVENTION An object of the present invention is to provide a high-pressure compressor that can be quickly restarted when the refrigeration cycle device is turned off and then restarted, and a refrigeration cycle device having the same.

Another object of the present invention is to perform a flat pressure operation for resolving the differential pressure between suction pressure and discharge pressure at the same time as the compressor is stopped when the refrigeration cycle device is turned off and the compressor is stopped. An object of the present invention is to provide a high-pressure compressor capable of rapidly restarting and a refrigeration cycle device having the same.

Another object of the present invention is to perform a flat pressure operation for resolving the differential pressure between the suction pressure and the discharge pressure at an appropriate time when the refrigeration cycle device is turned off and the compressor is stopped, so that the compressor can be operated quickly when the refrigerating cycle device is restarted. An object of the present invention is to provide a high-pressure compressor and a refrigeration cycle device having the same, which can be restarted.

Another object of the present invention is to provide a high-pressure compressor that allows the refrigeration cycle device to exchange heat when the refrigeration cycle device is turned off and the compressor is stopped, and a refrigeration cycle device having the same.

Another object of the present invention is to prevent the overload prevention device from being damaged in advance by enabling the compressor to be quickly restarted when the refrigeration cycle device is re-operated, and thereby prevent the motor from being overheated and damaged, thereby ensuring the reliability of the compressor. An object of the present invention is to provide a rotary compressor capable of increasing the temperature and a refrigeration cycle device having the same.

Another object of the present invention is to reduce the manufacturing cost and increase reliability by excluding the use of a solenoid valve, to miniaturize the compressor, and to have a high-pressure compressor having a flat pressure device that can be prevented from damage during operation, and a refrigeration cycle having the same It is intended to provide a device.

In order to achieve the object of the present invention, a flat pressure is applied between the inner space of the casing and the compression space of the compression unit when stopped using a mechanical on/off valve operated according to the difference between the pressure filled in the inner space of the casing and the pressure discharged from the compression unit. A high-pressure compressor and a refrigeration cycle device having the same may be provided.

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

In addition, a check valve may be installed in the discharge pipe of the casing to prevent the refrigerant discharged from the inner space of the casing toward the condenser from flowing back into the inner space of the casing through the discharge pipe.

In addition, in order to achieve the object of the present invention, a casing having a sealed inner space;

a driving motor provided in the inner space of the casing; a compression unit provided in the inner space of the casing, provided with a compression space for compressing the 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 the pressure of the inner space of the casing and the pressure of the compression space of the compression unit; a first valve for suppressing a reverse flow of the refrigerant discharged from the inner space of the casing into the inner space of the casing; a bypass pipe connecting the inner space of the casing and the suction side of the compression unit; And connected to the bypass pipe in the inside of the casing, selectively opening and closing the bypass pipe while moving between the first position and the second position according to the difference between the internal pressure of the casing and the pressure on the discharge side of the compression unit A high-pressure compressor comprising two valves may be provided.

Here, the second valve may be configured to block the bypass pipe when a compressive load is generated in the compression unit, while opening the bypass pipe when the compressive load is removed in the compression unit.

Here, the second valve is provided with a valve space, one side of the valve space is formed with a first hole communicating with the discharge side of the compression part, and the other side of the valve space is connected to the inner space of the casing. a valve housing in which a hole is formed and a third hole communicating with the bypass pipe is formed between the first hole and the second hole; and a valve plate inserted into the valve space of the valve housing and moved between the first and second positions according to a difference between the pressure supplied to the first hole and the pressure supplied to the second hole. have.

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

In addition, 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 smaller than or equal to a thickness in the moving direction of the valve plate.

In addition, the third hole may be formed to be closed together at a position where the second hole is closed by the valve plate.

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

In addition, the valve spring may be provided at the side of the second hole with the valve plate interposed therebetween.

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

In addition, a plurality of the outlets are provided so that the refrigerant compressed by the compression unit is discharged in both directions with respect to the axial direction based on the compression unit, and the refrigerant discharged from one of the plurality of outlets to the other outlet is provided in the compression unit. A plurality of refrigerant passages may pass through to be combined with the refrigerant discharged from the outlet, and the second valve may be installed to communicate with any one refrigerant passage among the plurality of refrigerant passages.

In addition, an inner diameter of a refrigerant passage in which the second valve is installed among the plurality of refrigerant passages may be greater than or equal to an inner diameter of other refrigerant passages.

And, the compression unit is provided with a single discharge port so that the refrigerant compressed in the compression unit is discharged in one direction with respect to the axial direction, the compression unit is provided with a discharge cover for accommodating the discharge port, the second valve is the discharge It may be provided on the cover.

In addition, in order to achieve the object of the present invention, a casing having a sealed inner space; a compression unit provided in the inner space of the casing, provided with a compression space for compressing the 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 open and close the discharge port according to a difference between the pressure of the inner space of the casing and the pressure of the compression space of the compression unit; a discharge cover having a discharge space to accommodate the discharge valve; a bypass pipe connecting the inner space of the casing and the suction side of the compression unit; A first hole communicating with the discharge space of the discharge cover, a second hole communicating with the inner space of the casing, and a third hole communicating with the bypass pipe are provided, the first hole, the second hole, and the third hole a valve housing having a valve space in which all holes are communicated; and the second position moving between the first position and the second position according to a difference between the pressure supplied through the first hole and the pressure supplied through the second hole, which is provided movably in the valve space of the valve housing. A high-pressure compressor comprising a; valve plate selectively opening and closing three holes may be provided.

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

And, the valve housing is fixedly coupled to the middle of the bypass pipe from the outside of the casing, and 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. It may communicate with the space or the inner space of the casing.

Here, a check valve for suppressing a reverse flow of the refrigerant discharged from the inner space of the casing into the inner space of the casing may be further provided.

In addition, in order to achieve the object of the present invention, a compressor; a condenser connected to the compressor; a condenser fan provided on 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 may be provided with a refrigeration cycle device including the high-pressure compressor described above.

A high-pressure compressor according to the present invention and a refrigeration cycle device to which the same is applied include a check valve that blocks a reverse flow of refrigerant discharged from the compressor toward the condenser back to the compressor, and between the inner space of the casing and the compression space of the compression unit when the compressor is stopped. By installing a bypass valve for resolving the pressure difference, in a refrigeration cycle device to which a high-pressure compressor such as a rotary compressor is applied, when the refrigeration cycle device is stopped, the suction side and the discharge side of the compressor can quickly achieve a flat pressure. When the refrigeration cycle device is restarted, the compressor can be restarted quickly.

In addition, it is possible to increase the reliability of the compressor by preventing damage to the overload prevention device and the motor that may occur when restarting the compressor is not smooth after stopping the refrigeration cycle device.

In addition, as the bypass valve consists of a mechanical valve that operates by the difference between the pressure in the internal space of the casing and the pressure in the compression space, power consumption and a separate control unit for the bypass valve are not required, thereby reducing the manufacturing cost. Reliability degradation due to malfunction can be prevented in advance. In addition, since the bypass valve can be installed inside the casing, the compressor can be miniaturized and damage during transportation can be prevented in advance.

In addition, a so-called differential pressure operation in which a fan of the refrigeration cycle device is operated to continue heat exchange while the compressor is stopped can be performed, thereby increasing the energy efficiency of the refrigeration cycle device.

1 is a schematic diagram showing a refrigeration cycle device according to the present invention;
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 longitudinal sectional view and an exploded perspective view respectively showing a first valve and a second valve in the compressor according to FIG. 2;
5 and 6 are cross-sectional views showing assembling embodiments of the second valve according to FIG. 4;
7A and 7B are cross-sectional views showing the operation of the second valve according to on/off of the compressor in the second valve according to FIG. 4;
8A to 8C are schematic views for explaining a differential pressure operation, a flat pressure operation, and a restart operation in the refrigeration cycle device according to FIG. 2;
9A to 10B are a block diagram showing the operation of the conventional rotary compressor and the rotary compressor of the present invention, and a graph showing the pressure change and the current change therefor. FIGS. 9A and 9B are views showing the conventional rotary compressor, , Figures 10a and 10b are views shown for the present invention,
11A and 11B are graphs showing a refrigeration cycle device to which the rotary compressor of the present invention is applied compared to a refrigeration cycle device to which a conventional rotary compressor is applied, and FIG. 11A is a conventional rotary compressor and the rotary compressor of the present invention at the same load When stopped during operation, it is a graph showing the relative comparison of the latent heat section, and FIG. 11b is a graph showing the comparison of the restart time and stabilization stage for the conventional rotary compressor and the rotary compressor of the present invention;
12 to 14 are schematic views showing an installation form of a second valve according to a type of a rotary compressor according to the present invention;
15 and 16 are schematic views showing other embodiments of the connection position of the bypass pipe in the refrigeration cycle device according to FIG.

Hereinafter, a compressor according to the present invention, a refrigeration cycle device to which the same is applied, and a method of operating the refrigeration cycle device will be described in detail based on an embodiment shown in the accompanying drawings.

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

Referring to FIG. 1 , the refrigeration cycle apparatus according to this embodiment includes a compressor 1 , a condenser 2 , an expansion valve 3 , and an evaporator 4 . When this refrigeration cycle device 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 installed between the discharge side and the suction side of the compressor 1 to convert the circulation direction of the refrigerant discharged from the compressor 1 to an outdoor unit or an indoor unit, and to operate the refrigeration cycle device. It can be switched for cooling or heating. 1 is a schematic diagram in which a refrigerant switching valve is not shown, and a cooling case is taken as an example.

The high-pressure refrigerant discharged from the compressor (1) moves to the condenser (2) installed in the outdoor unit, the refrigerant is condensed in the condenser (2) and expanded while passing through the expansion valve (3), and the expanded refrigerant is transferred to the indoor unit A series of circulation processes that are sucked back into the compressor 1 in an evaporated state through the installed evaporator 4 are repeated. Here, the compressor 1 may be configured as a rotary compressor in which the inner space of the casing is in a high-pressure discharge pressure state.

Referring to FIG. 2 , in the rotary compressor 1 according to this embodiment, an electric part is installed in the inner space of the compressor casing 10 , and the refrigerant is sucked and compressed on the lower side of the electric part 20 and then the casing 10 ) is provided with a compression unit 30 for discharging to the inner space (10a). The electric part 20 and the compression part 30 are mechanically connected by a rotating shaft 23 .

In the electric part 20 , the stator 21 is press-fitted to the inside of the compressor casing 10 and fixed, and the rotor 22 is rotatably inserted into the stator 21 . A rotating shaft 23 is press-fitted to the center of the rotor 22 .

In the compression unit 30 , a main bearing 31 supporting the rotating shaft 23 is fixedly coupled to the inner circumferential surface of the compressor casing 10 , and the lower side of the main bearing 31 is a rotating shaft 23 together with the main bearing 31 . ) is provided, and between the main bearing 31 and the sub-bearing 32, a cylinder forming a compression space 33a together with the main bearing 31 and the sub-bearing 32 (33) is provided. The cylinder 33 is fixed by bolting to the main bearing 31 together with the sub bearing 32 .

And the compression space (33a) of the cylinder (33) is provided with a rolling piston (34) coupled to the eccentric portion of the rotating shaft (23) and compressing the refrigerant while rotating, and a rolling piston (34) is provided on the inner wall of the cylinder (33). ) in contact with the rolling piston 34 and the vane 35 dividing the compression space 33a into the suction chamber and the compression chamber 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, and a first discharge port 31a for opening and closing the first discharge port 31a is formed at an end of the first discharge port 31a A valve 36 is installed. A first discharge cover 37 having a first discharge space 37a is installed on the upper surface of the main bearing 31 .

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

And, in the compression unit 30, the refrigerant discharged to the second discharge space (39a) to move to the first discharge space (37a) or to guide the space between the compression unit (30) and the electric unit (20) A plurality of refrigerant passages (30a, 30b) are formed. As many refrigerant passages as possible, the refrigerant discharged to the second discharge space (39a) can be rapidly moved toward the discharge pipe (16). The figure shows an example of a first refrigerant passage 30a and a second refrigerant passage 30b.

The first refrigerant passage 30a and the second refrigerant passage 30b are respectively formed to pass through the sub bearing 32 , the cylinder 33 , and the main bearing 31 in the axial direction. 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, it may be advantageous for mounting the second valve 130 to be described later if the second refrigerant passage 30b is formed to be exposed to the outside of the first discharge cover 30a as much as possible. The second valve will be described later.

In addition, the inner diameter (D1) of the first refrigerant passage (30a) and the inner diameter (D2) of the second refrigerant passage (30b) may be formed to be the same. 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 formed to be different.

For example, the first refrigerant passage 30a is simply 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, 2 In the case of mounting a second valve 130 to be described later in the refrigerant passage 30b, the inner diameter D2 of the second refrigerant passage 30b is larger than the inner diameter D1 of the first refrigerant passage 30a. When the compressor is restarted, it is preferable because it can overcome the weight of the second valve plate 132 to be described later and quickly move the second valve plate 132 to the second position (bypass pipe closing position) P2 to be described later. can

The first discharge valve 36 and the second discharge valve 38 have the internal pressure (hereinafter, suction pressure) Ps of the compression space 33a and the internal pressure (hereinafter referred to as the suction pressure) Ps of the internal space 10a of the compressor casing 10 . , the discharge pressure) (Pd) may be opened and closed according to the difference. Therefore, if the suction pressure Ps is too low, the pressure difference between the suction pressure Ps and the discharge pressure Pd becomes too large, and this causes the suction pressure Ps to become the dischargeable pressure (the discharge valve can be opened). pressure) is not reached, and the refrigerant in the compression space 33a cannot be discharged. Then, while overload is applied to the electric part (hereinafter, mixed with the motor) 20 , the overload prevention device 50 provided in the electric part 20 operates to stop the motor to remove the compression load from the compression part 30 . will do

On the other hand, the compressor casing 10 has a cylindrical body 11 having both upper and lower ends opened, and an upper cap 12 and a lower cap 13 that cover the upper and lower ends of the cylindrical body 11 to seal the inner space 10a. can be made with A suction pipe 15 connected to the outlet side of the accumulator 40, which will be described later, is coupled to the lower half of the cylindrical body 11, and the upper cap 12 has a discharge side refrigerant pipe (L1) on the inlet side of the condenser 2 to be described later. A discharge pipe 16 connected to may be coupled. The suction pipe 15 penetrates the cylindrical body 11 and is directly connected to the suction port 33b of the cylinder 33, and the discharge pipe 16 penetrates the upper cap 12 to the inner space of the compressor casing 10 ( 10a) can be connected.

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 in the accumulator 40 to have a predetermined volume. can be The upper part of the accumulator 40 is connected to the evaporator 4 and the suction-side refrigerant pipe L2, and the lower part of the accumulator 40 is a suction pipe 15 connected to the cylinder 33 of the compressor casing 10. Can be connected 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 an L-shape, penetrates the lower surface of the accumulator (40), and the internal space (40a) of the accumulator (40) ) can be connected by being inserted as deep as a predetermined height inside.

The rotary compressor according to the present embodiment as described above operates as follows.

That is, when power is applied to the stator 21, the rotor 22 and the rotating shaft 23 rotate inside the stator 21 and the rolling piston 34 makes a swivel motion, and the rolling piston 34 rotates. The volume of the suction chamber is changed according to the turning movement of the , and the refrigerant is sucked into the cylinder (33).

This refrigerant is compressed by a compression load in the compression space 33a generated by the rolling piston 34 and the vanes 35, and the first discharge port 31a provided in the main bearing 31 and the sub bearing 32 are compressed. It is discharged to the first discharge cover 37 and the second discharge cover 39 through the second discharge port 32a, respectively.

Then, the refrigerant discharged to the first discharge cover 37 is directly discharged to the inner space 10a of the casing 10 , while some of the refrigerant discharged to the second discharge cover 39 is the first refrigerant passage 30a ) through the discharging space 37a of the first discharging cover 37 or moving to the inner space 10a of the casing 10 . However, a portion 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 and a second valve plate 132 to be described later. ) by pressing, the bypass pipe 120 to be described later is blocked. This will also be described later.

On the other hand, the refrigerant that has moved into the inner space 10a of the casing 10 through the first refrigerant passage 30a is discharged to the refrigerating cycle device through the discharge pipe 16, and the refrigerant discharged to the refrigerating cycle device is a condenser It flows into the accumulator 40 through (2), the expansion valve 3 and the evaporator 4, and this refrigerant passes through the accumulator 40 before being sucked into the compression space 33a of the cylinder 33, The oil is separated from the gas refrigerant, and 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 the compressed space of the cylinder (33) (33a) repeats a series of inhaled processes.

At this time, the condensing fan 2a and the evaporating fan 4a are operated to increase the ambient temperature in the condenser 2 while the evaporator 4 lowers the ambient temperature.

On the other hand, when the operation of the refrigeration cycle device is stopped, the compressor 1 is also stopped (OFF) so that no more refrigerant is discharged from the compressor 1 in the condenser direction. However, the refrigerant discharged from the compressor (1) to the refrigeration cycle device is the evaporator ( 4) It moves in the direction. Therefore, even when the compressor 1 is stopped, that is, the compression load of the compression unit 30 is removed, when the condensation fan 2a and the evaporation fan 4a of the refrigeration cycle device are operated, the refrigerant moves according to the pressure difference. The heat exchange in the condenser 2 and the evaporator 4 can be continued by using the latent heat during the operation, thereby increasing the efficiency of the refrigeration cycle device.

However, the rotary compressor as described above cannot be restarted even when the pressure difference between the suction pressure (pressure in the compression space) (Ps) and the discharge pressure (pressure in the casing inner space) (Pd) is small within 1 kgf/cm 2 due to the characteristics of the rotary compressor as described above. The time required should be long. However, if the time required for balancing is extended, oil leakage increases, so in reality, it is impossible to extend the time required for balancing. Therefore, it is necessary to shorten the time required for balancing pressure as possible. Then, since the compressor 1 has not yet reached the balancing pressure required for restart, the compressor 1 cannot be restarted even if the refrigerating cycle device is to be restarted. However, if the balancing time required is set to be short, the latent heat in the differential pressure section may not be sufficiently used, and thus energy efficiency may be lowered.

In consideration of this, in this embodiment, a check valve (hereinafter, the first valve) 110 is installed at the inlet end or inlet side of the discharge pipe 16 in the internal space 10a of the compressor casing 10, and the refrigerant is discharged from the compressor. A bypass for selectively opening and closing the bypass pipe 120 and the bypass pipe 120 between the inlet end of the first valve 110 and the suction side of the accumulator 40 based on the discharge direction in (1) By installing the valve (hereinafter, referred to as the second valve) 130 , it is possible to increase energy efficiency by sufficiently utilizing latent heat while shortening the flat pressure time when the compressor is stopped.

For convenience, a flow path connecting between the discharge side and the suction side with respect to the compression unit is referred to as a first refrigerant flow path Q1, and a flow path connecting both ends of the first refrigerant flow path Q1 by bypassing each other is a second refrigerant flow path. It is called (Q2). One end of the second refrigerant passage Q2 is connected to the discharge side with respect to the compression unit (exactly, the discharge valve) 30 , and the other end of the second refrigerant passage Q2 is connected to the suction side with respect to the compression unit 30 . can be connected

For example, the first refrigerant flow path Q1 has one end of the inner space ( Assuming that from 10a) to the compression space 33a of the cylinder 33 on the suction side, the refrigerant discharged to the inner space 10a of the compressor casing 10 is the first refrigerant passage Q1 through the condenser 2 and the expansion valve. (3) and can be said to be a flow path connected to the compression space (33a) including the refrigeration cycle device consisting of the evaporator (4).

In addition, the second refrigerant passage Q2 includes the internal space 10a of the compressor casing 10 and the compression unit 30 based on the first discharge valve 36 and the second discharge valve 38 of the compression unit 30 . ) between the compression space (33a), the condenser (2), the expansion valve (3), and can be said to be a flow path directly connected without passing through the evaporator (4).

Here, the second refrigerant passage Q2 is provided in the inner space 40a of the second valve 130 and the accumulator 40 provided in the inner space 10a of the compressor casing 10 as shown in FIGS. 1 and 2 . It may be made of a bypass pipe 120 to which both ends are respectively connected.

3 to 5 are longitudinal sectional views respectively showing a first valve and a second valve in the compressor of 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 . Accordingly, compared to that the first valve 110 is installed in the discharge pipe 16 from the outside of the casing 10, it is possible to substantially reduce the internal volume of the compressor 1, thereby further reducing the time required for flat pressure. .

Here, when the first valve 110 stops the compressor 10, that is, when the refrigerant discharged from the compressor casing 10 toward the condenser 2 10) may be formed of a one-way valve capable of blocking the reverse flow into the inner space (10a). Of course, the first valve 110 may be formed of an electromagnetic valve, but a mechanical valve may be suitable in consideration of cost or reliability.

3, the first valve 110 is a first valve housing 111 that is installed to communicate with the inlet end or the inlet side of the discharge pipe 16 in the inner space 10a of the compressor casing 10, The first valve plate 112 is accommodated in the first valve space 115c of the first valve housing 111 and moves according to the pressure difference between the two sides to open and close the first valve housing 111 .

The first valve housing 111 may be formed as a single body. However, since the first valve plate 112 must be 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 to form the first It is preferable to form a valve space (111a).

Both ends of the first housing body 115 are opened to form a condenser-side open end (first open end) 115a and a compressor-side open end (second open end) 115b. Accordingly, the first open end 115a and the second open end 115b have a first valve space 111a in which the first valve plate 112 can move is formed to be expanded.

The discharge pipe 16 is connected to the first opening end 115a of the first housing body 115, and the first valve cover 116 is inserted and coupled to 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 .

The first valve plate 112 may be formed in a piston shape, but since the first valve plate 112 opens and closes the through hole 116a of the first valve cover 116 on one side thereof, it is formed as a thin plate body. This may be preferable in consideration of valve responsiveness and the like.

In addition, the first valve plate 112 has a gas communication groove 112a formed in its central portion. Accordingly, when the first valve plate 112 is in contact with the first open end 115a, the first open end 115a is opened, while the first valve plate 112 is the second open end 115b. When in contact with the through hole (116a) of the second valve cover (116) provided at the second open end (115b) is completely blocked.

On the other hand, as described above, a bypass pipe 120 is connected between the second discharge cover 39 and the accumulator 40, and one end of the bypass pipe 120 is a second valve ( 130) is installed.

As for the second valve 130, when the compressor 1 is stopped and the compression load in the compression space 33a is removed, the second valve 130 is opened at the same time that the compressor is stopped, and the compressor 1 is restarted and the compression space 33a is removed. ) when a compression load occurs, the second valve 130 is closed at the same time 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, and a second valve housing 131 . It is inserted into the valve space (131a) of the second valve plate (132) for selectively opening and closing the bypass pipe (120).

The second valve housing 131 may be formed as a single body. However, since the second valve plate 132 must be inserted into the second valve space 131a, the second valve housing 131 has the second housing body 135 and the second valve like the first valve housing 111 . It is preferable that the cover 136 is assembled to form the second valve space 131a.

The second housing body 135 has a second valve space 131a therein so that the second valve plate 132 can move according to a pressure difference. Accordingly, the second valve space 131a is formed to have a length such that the third hole 136a to be described later can be opened and closed while the second valve plate 132 moves in the longitudinal direction.

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

In addition, the second housing body 135 may be inclined so that the inner surface of the side where the first hole 135a communicates becomes narrower in the direction of the first hole. Accordingly, comparing the area where both sides of the second valve plate 132 are exposed to the refrigerant in the state that the second valve plate 132 is moved to the first position (P1) toward the first hole 135a It can be formed almost identically, that is, the lower surface (hereinafter, the first surface) 132a facing the first hole 135a at the first position P1 is the upper surface (hereinafter, the second surface) that is the opposite surface (hereinafter, the second surface) ( 132b), so that when the compressor is restarted, the refrigerant supplied through the first hole 135a can pressurize the entire first surface 132a of the second valve plate 132 Therefore, even if the second valve plate 132 receives the discharge pressure of the inner space of the casing on the second surface, it is possible to quickly move toward the second hole (136a).

The interval between the first hole 135a and the second hole 136a is the second valve plate 132 in the longitudinal direction of the second valve housing 131 in the first position P1 and the second position (( P2) while moving between the third hole (135b) is formed to have a distance that can be opened and closed.

In addition, the cross-sectional area of the first hole 135a may be the same as the cross-sectional area of the second hole 136a, but in order for the second valve plate 132 to quickly open the bypass pipe when the compressor is stopped, the second hole It may be preferable that the cross-sectional area of the 136a is larger than the cross-sectional area of the first hole 135a. For example, when the cross-sectional area of the first hole 135a is formed to be larger than that of the second hole 136a, the second valve plate 132 facing the first hole 135a even when the compressor stops operating. The first surface 132a may receive a higher pressure than the second surface 132b of the second valve plate 132 facing the second hole 136a. Then, as the descending speed of the second valve plate 132 is delayed, the third hole 135b communicating with the bypass pipe may not be opened quickly.

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

In addition, the third hole 135b is provided on the peripheral wall surface of the second housing body 135 and is formed in a direction crossing the center line of the first hole 135a or the second hole 136a, and the third hole 135b ) has an inner diameter that is smaller than or equal to the thickness of the second valve plate 132 in the moving direction. Accordingly, when the second valve plate 132 reaches the first position (P1) blocking the first hole 135a as shown in FIG. 7A , the third hole 135b is in an OPEN state, and FIG. 7B As such, when the second valve plate 132 reaches the second position (P2) blocking the second hole 136a, the third hole 135b is closed by the side surface of the second valve plate 132 (CLOSE). ) state, that is, the third hole 135b is formed to be closed together at the position where the second hole 136a is closed by the side surface 132c of the second valve plate 132 .

Meanwhile, the inner diameter D3 of the bypass pipe 120 may be the same as or smaller than the inner diameter D4 of the discharge pipe 16 or the discharge-side refrigerant pipe L1 or the suction-side refrigerant pipe L2. When the inner diameter D3 of the bypass tube 120 is larger than the inner diameter D4 of the discharge tube 16 or the discharge-side refrigerant tube or the suction-side refrigerant tube L2, the refrigerant flow rate is lowered and the time required for flat pressure is reduced. Not only is it delayed, but the size of the second valve 130 must be increased by that much, so the cost may increase.

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

Referring to FIG. 8A , when the compressor is stopped, the refrigerant discharged from the inner space 10a of the compressor casing 10 in the condenser direction through the discharge pipe 16 flows back into the inner space 10a of the compressor casing 10 . However, this may be suppressed by the first valve 110 . Through this, the refrigerant can move only in the direction of the accumulator 40 through the expansion valve 3 and the evaporator 4 in the condenser 2 according to the pressure difference. At this time, when the condenser fan 2a or the evaporator fan 4a is operated, the refrigerant passing through the condenser 2 and the evaporator 4 can exchange heat with air even when the compressor 1 is stopped. energy efficiency can be improved.

Next, referring to FIG. 8B , as the compressor 1 is stopped, the second valve 130 is opened (OPEN) as shown in FIG. 8A to open the bypass pipe 120 . 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 .

Then, as shown in FIG. 7A , the refrigerant remaining in the second discharge space 39a of the second discharge cover 39 is the first refrigerant passage 30a according to the pressure difference with the inner space 10a of the casing 10 . through the first discharge space (or the inner space of the casing) 37a. And, a portion of the refrigerant remaining in the second discharge space (39a) of the second discharge cover (39) through the second refrigerant passage (30b) close to the first hole (135a) of the second valve housing (131) It moves to the 1st position (P1). However, the pressure of the refrigerant moving to the first hole 135a is lowered, so that it is impossible to push up the second valve plate 132, so that the second valve plate 132 is It descends by its own weight (or the restoring force of the valve spring) and the internal pressure of the casing 10 flowing in through the second hole 136a to block the first hole 135a. At the same time, the third hole 135b This is opened (OPEN), the bypass pipe 120 is opened.

Then, some of the refrigerants discharged to the compressor casing 10 do not move in the condenser direction, but 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 . Due to the difference, it moves toward the bypass pipe 120 and moves to the internal space 40a of the accumulator 40 . Then, the pressure in the inner space 40a of the accumulator 40 and the pressure in the inner space 10a of the compressor casing 10 achieve a flat pressure within a predetermined range (normally, within 1 kgf/cm 2 ).

Then, the compressor 1 maintains the suction pressure Ps and the discharge pressure Pd in a flat pressure state in which the compressor can be started, so that the compressor 1 can be in a state waiting for restart. Accordingly, the internal pressure of the compressor casing is further lowered, so that the first valve is quickly closed to prevent the refrigerant discharged in the condenser direction from flowing back into the compressor.

Next, referring to FIG. 8c , when the user selects to restart the refrigeration cycle device that is temporarily stopped, as shown in 8b above, the suction pressure (Ps) and the discharge pressure (Pd) become a flat pressure state, the compressor (1) is quickly restarted. Then, 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 . At this time, as shown in FIG. 7B , a portion of the refrigerant discharged to the second discharge space 39a of the second discharge cover 39 is part of the first hole 135a of the second valve housing 131 through the second refrigerant passage 30b. ) will be moved to The refrigerant moving to the first hole 135a pushes the second valve plate 132 in the direction of the second hole because the internal pressure of the second discharge cover 39 is relatively high compared to the internal pressure of the casing 10 . is raised, 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 pipe 120 is closed so that the refrigerant discharged into the inner space 10a of the compressor casing 10 is blocked from being bypassed in the accumulator direction, thereby increasing the internal pressure of the compressor casing 10 .

Then, the first valve 110 is opened (OPEN) according to the pressure difference between the internal pressure of the casing 10 and the inlet side of the condenser 2, and thus the refrigerant discharged into the internal space of the compressor casing 10 is discharged in the condenser direction through the discharge pipe 16, so that the refrigeration cycle device can be smoothly restarted.

9A to 10B are a block diagram showing the operation of the conventional rotary compressor and the rotary compressor of the present invention, and a graph showing the pressure change and the current change therefor. FIGS. 9A and 9B are views showing the 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 a refrigeration cycle apparatus, when the compressor is stopped, the discharge pressure Pd is continuously lowered and the suction pressure Ps is temporarily increased and maintained.

Here, when the user operates the refrigeration cycle device and power is applied to the compressor, the pressure difference inside the compressor, that is, the differential pressure ( ΔP ) between the suction pressure (Ps) and the discharge pressure (Pd) is equal to the flat pressure condition (normally, 1 kgf). /cm2), the compressor will immediately resume operation.

However, if the pressure difference inside the compressor is greater than the flat pressure condition, the compressor cannot start, and thus the refrigerant gas cannot be compressed and discharged. Then, while overcurrent is generated in the driving motor, which is the electric part, the overload prevention device 50 operates to cut off the power supplied to the driving motor. Then, after the return time of the overload prevention device 50 elapses, the overload prevention device 50 returns and power is applied to the driving motor again. However, if the pressure inside the compressor still does not satisfy the flat pressure condition, the previous operation is repeated. As described above, since the conventional rotary compressor takes a long time to reach the flat pressure condition, this process is repeated several times.

This is shown in a graph as shown in FIG. 9B. That is, when the compressor is stopped, the refrigerant discharged from the compressor (1) flows into the compressor through all the refrigeration cycles leading to the condenser (2), the expansion valve (3), and the evaporator (4), so the discharge pressure (solid line) is gently will decrease As a result of the experiment, it was found that it takes about 20 minutes for the compressor to reach the pressure condition (equilibrium pressure condition) for restarting.

In addition, a restart current is supplied to the driving motor as shown in the graph below in FIG. 9B until the flat pressure condition is reached, but as the compressor fails to restart several times, a high peak point of the current appears periodically. The point at which this peak appears is a point at which the overload protection device 50 operates, and between these peak points is a section in which the overload protection device 50 returns again. As shown in the figure, the distance between the peak points gradually increases, because the overload prevention device 50 overheats as the compressor repeatedly fails to restart, and the return time is delayed by that much. Therefore, it can be seen that the overload prevention device 50 for preventing overload of the motor repeatedly operates a number of times as current is continuously applied to the driving motor even though the compressor has not yet reached the normal pressure condition for restarting it. can

On the other hand, referring to FIG. 10A , even when the rotary compressor of this embodiment is applied to a refrigeration cycle apparatus, when the compressor is stopped, the discharge pressure is temporarily lowered and the suction pressure is temporarily increased. Thereafter, when the discharge pressure rises and the suction pressure decreases so that the pressure difference exceeds a predetermined range, the second valve 130 is switched to an open state according to the pressure difference.

Then, while the bypass pipe 120 is opened, a part of the refrigerant remaining in the internal space 10a of the compressor casing 10 moves to the suction side, which is a low pressure part, through the bypass pipe 120, so that the suction pressure inside the compressor ( Ps) and the discharge pressure Pd quickly satisfy the flat pressure condition.

At this time, when the user operates the refrigeration cycle device and power is applied to the electric part 20 of the compressor, the pressure difference inside the compressor is already in a state that the flat pressure condition (normally, within 1 kgf/cm 2 ) is satisfied, so the compressor is operated immediately. will resume Of course, the compressor may not be restarted all at once for other reasons, but the restart failure is much less than that of a conventional rotary compressor. This can also be confirmed through FIG. 10B. For reference, FIG. 10b is a graph obtained by testing whether the compressor is restarted by repeatedly turning on/off the refrigeration cycle device several times during the same time period as in FIG. 9b.

As shown in this figure, when the compressor is stopped, the discharge pressure (thick solid line) is momentarily lowered, and the suction pressure is temporarily increased and then maintained constant.

At this time, as the second valve 130 operates and the bypass pipe 120 is opened, a portion of the refrigerant discharged into the internal space 10a of the compressor casing 10 based on the compression unit is transferred to the accumulator through the bypass pipe 120 . As it moves to the inner space 40a of 40, the discharge pressure Pd and the suction pressure Ps inside the compressor quickly reach the flat pressure condition, and thereby the inner space 10a of the compressor becomes an intermediate pressure (thin It can be seen that a solid line is formed.

Accordingly, as shown by a thick solid line in FIG. 10B , it can be seen that the compressor of the present invention restarts several times during the same period of time as compared to FIG. 9B while the discharge pressure Pd fluctuates several times.

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

In this way, when the refrigeration cycle device is stopped, the compressor is stopped and at the same time the suction pressure and the discharge pressure can quickly equalize the pressure, so that the compressor can be restarted smoothly. Failure of the overload protection device can be prevented in advance by not repeating it. In addition, the reliability of the compressor may be improved by preventing the driving motor from being overheated due to overcompression and thus from being damaged by the driving motor.

In addition, even if the refrigeration cycle device to which a high-pressure compressor such as a rotary compressor is applied is temporarily stopped, the so-called differential pressure operation of operating the fan of the refrigeration cycle device during the stopped time can be continued, thereby increasing the energy efficiency of the refrigeration cycle device. have. This can be seen through FIGS. 11A and 11B . 11A is a graph showing a relative comparison of latent heat sections when the conventional rotary compressor and the rotary compressor of the present invention are stopped while operating under the same load, and FIG. 11B is a restart time of the conventional rotary compressor and the rotary compressor of the present invention and a graph showing the comparison of stabilization steps.

11A , it can be seen that the suction pressure suddenly increases when the compressor is stopped and then increases gently thereafter. On the other hand, it can be seen that the discharge pressure suddenly decreases when the compressor is stopped and then decreases gently thereafter.

In this case, in the conventional case, a portion of the refrigerant discharged from the compressor flows backward from the condenser side toward the relatively low pressure compressor due to the pressure difference when the compressor is stopped, and this reverse flow refrigerant has a relatively higher pressure than the refrigerant remaining in the inner space of the compressor casing. will achieve Then, the refrigerant remaining in the inner space of the compressor casing is pushed out, and the pushed refrigerant leaks in the direction of the accumulator through the gap between the members constituting the compression part. Accordingly, in the conventional rotary compressor, the suction pressure abruptly increases, whereas the discharge pressure decreases rapidly as some 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 to block the refrigerant from flowing back from the condenser to the compressor, so that the suction pressure is low and the discharge pressure is high compared to the conventional compressor seen above. state can be maintained. In addition, as the change range of the suction pressure and the discharge pressure is relatively low, the latent heat usage rate in the same section is increased by approximately 35%. This is the shaded area in FIG. 11A.

Therefore, in terms of heat exchange efficiency in a unitary refrigeration cycle device, the size of the heat exchangeable section and the pressure difference in a state where the compressor is stopped is large, and the present invention is improved compared to the prior art, reducing power consumption and increasing energy efficiency. do.

In addition, in the conventional case, as the refrigerant leaks from the compressor casing in the direction of the accumulator and the oil remaining in the compressor casing is also pushed out, an oil shortage may be caused in the internal space of the compressor casing. Although friction loss may increase during operation, the present invention can also reduce friction loss due to this reason, thereby further increasing energy efficiency.

Meanwhile, referring to FIG. 11B , when the conventional rotary compressor is applied, as described above, the refrigerant discharged from the compressor circulates through the condenser, the expansion valve, and the evaporator, so that the compressor can be restarted, that is, the suction pressure and the discharge pressure. The time required to satisfy the flat pressure condition (differential pressure: within 1 kgf/cm 2 ) (the time required for flat pressure) is much longer than that of the present invention. Accordingly, the restart possible time for the conventional rotary compressor becomes significantly later than the restartable time for the rotary compressor of the present invention. Therefore, when the user uses the conventional rotary compressor, even if the user tries to operate the refrigeration cycle device again, the refrigeration cycle device cannot quickly resume operation as the compressor is not restarted quickly. problems such as

On the other hand, in the present invention, as described above, as the pressure is preliminarily performed using the bypass pipe 120 and the second valve 130 at the same time as the compressor is stopped, a separate leveling time is unnecessary or even necessary, in the prior art. much shorter than Accordingly, when the user wants to restart the refrigeration cycle device, the compressor is quickly restarted, so that the refrigeration cycle device can enter the normal operation much faster than in the related art. Therefore, the present invention can be much improved in energy efficiency compared to the prior art.

In addition, even looking at the stable load section of the refrigeration cycle device, it can be seen that the present invention enters the stabilization phase much faster than in the prior art. Through this, it can be seen that the energy efficiency of the refrigeration cycle device to which the rotary compressor of the present invention is applied can be improved compared to the refrigeration cycle device to which the conventional rotary compressor is applied.

In addition, as in the present invention, as the second valve constituting the bypass valve is a mechanical valve that operates by the difference between the pressure in the inner space of the casing and the pressure in the compression space, power consumption for the second valve and a separate control unit This eliminates the need for manufacturing costs and reduces reliability due to malfunctions in advance. In addition, since the second valve can be installed inside the casing, it is possible to miniaturize the compressor and prevent the second valve from being damaged during transportation.

On the other hand, 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, the same second valve as in the above-described embodiment may be applied even when the compressor is discharged in one direction.

For example, as shown in FIG. 12 , when the discharge port 31a is formed only on the main bearing 31 , the second valve 130 provided in the main bearing 31 may be installed on the discharge cover 37 . Accordingly, the first hole 135a of the second valve 130 communicates with the discharge space 37a of the discharge cover 37 . In this case, the second valve housing 131 of the second valve 130 may be installed to contact the discharge cover 37 . However, the second valve housing 131 is fixed to the inner circumferential surface of the casing 10 and the like and is a separate connection pipe, the first hole 135a of the second valve housing 131 and the discharge space 37a of the discharge cover 37. can also be connected.

However, in this case, since the discharge space (37a) of the discharge cover (37) is located adjacent to the inner space (10a) of the casing (10), between the inner pressure of the discharge cover (37) and the inner pressure of the casing (10) The pressure difference 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, the discharge through-hole (not shown) of the discharge cover 37 communicating with the inner space 10a of the casing 10 ), or the cross-sectional area of the second hole 136a may be smaller and longer than the cross-sectional area of the first hole 135a.

Since the basic configuration or effect of the compressor according to the present embodiment as described above or the basic configuration or effect of the refrigeration cycle apparatus including the same are substantially the same as those of the above-described embodiment, a detailed description thereof will be omitted.

On the other hand, another embodiment of the rotary compressor according to the present invention is as follows.

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

For example, as shown in FIG. 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 . It is connected to the tube 120 and fixedly coupled, and the first hole 135a and the second hole 136a are connected to the second discharge cover 37 by the respective connecting tubes 141 and 142 penetrating the casing 10 . ) may be in communication with the second discharge space 37a 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 in occupational communication with the discharge space of the discharge cover or the inner space of the casing without a separate connection pipe.

Since the basic configuration or effect of the compressor according to the present embodiment as described above or the basic configuration or effect of the refrigeration cycle apparatus including the same are substantially the same as those of the above-described embodiment, a detailed description thereof will be omitted. However, in the case of this embodiment, as the second valve is installed outside the casing, it may be advantageous for maintenance of the second valve.

On the other hand, another embodiment of the rotary compressor according to the present invention is as follows.

That is, in the above-described embodiment, in the vertical rotary compressor in which the casing is perpendicular to the ground, the second valve coincides with the axial direction of the rotary compressor. However, the casing may be installed horizontally or with a sand type. Even in this case, it is preferable that the second valve be 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 orthogonal to the axial direction of the rotation shaft 23 . This is that the second valve 130 of this 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 and the second valve plate 132 is used together with the elastic force of the valve spring in addition to the differential pressure described above, the second valve is necessarily perpendicular to the axis of rotation, That is, it does not need to be arranged in a direction perpendicular to the ground.

Since the basic configuration or effect of the compressor according to the present embodiment as described above or the basic configuration or effect of the refrigeration cycle apparatus including the same are substantially the same as those of the above-described embodiment, a detailed description thereof will be omitted. However, in this embodiment, it is possible to increase energy efficiency by operating the refrigeration cycle even when the compressor is stopped while diversifying the installation form of the compressor according to the conditions and achieving a rapid equilibrium pressure when the compressor is stopped to prevent delay in restarting.

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

That is, in the above-described embodiment, the first valve was installed in the discharge pipe in the inner space of the casing. However, the first valve may be installed 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 operational effects are substantially the same as those of the above-described embodiment, and thus a detailed description thereof will be omitted. However, in this case, as the first valve 110 is installed outside the casing 10 , maintenance of the first valve 110 may be advantageous.

Also, as shown in FIG. 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 in advance the phenomenon in which the first valve 110 is not opened even when the second valve 130 remains closed when the compressor 1 is stopped.

On the other hand, in the rotary compressor according to the present invention, another embodiment with respect to the branching position of the bypass pipe is as follows.

That is, in the above embodiment, the outlet end of the bypass pipe communicates with the internal space of the accumulator, but in this embodiment, the outlet end of the bypass pipe 120 is connected to the suction pipe 15 as shown in FIG. 16 . .

In this case, as the inner space 10a of the casing 10 directly communicates with the suction pipe 15, the time required for flat pressure can be further reduced. However, since oil or liquid refrigerant discharged into the inner space 10a of the casing 10 can directly flow into the compression space 33a without passing through the inner space 40a of the accumulator 40, the bypass pipe 120 It may be preferable that an oil separator or a liquid refrigerant separator 125 is provided at the inlet end of the .

On the other hand, in the above-described embodiment, the rotary compressor is limited to being applied only to a single operation mode in which only a power operation including a stop is applied. The same may be applied to the case of the driving mode.

For example, if the power operation is a state in which the compressor is driven and a pressure load is generated, and the stop is the state in which the compressor is turned off and the pressure load is removed, in the idling operation, the compressor is driven but does not work. It can be said that the load is removed.

Accordingly, when the first valve, the bypass pipe, and the second valve presented in the above-described embodiment are applied, even in the case of an idling operation, it is possible to achieve a flat pressure state between the suction side and the discharge side of the compression unit, if necessary.

Claims (17)

a casing having an enclosed inner space;
a driving motor provided in the inner space of the casing;
a compression unit provided in the inner space of the casing, provided with a compression space for compressing the 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 the pressure of the inner space of the casing and the pressure of the compression space of the compression unit;
a first valve for suppressing a reverse flow of the refrigerant discharged from the inner space of the casing into the inner space of the casing;
a bypass pipe connecting the inner space of the casing and the suction side of the compression unit; and
A second second connected to the bypass pipe inside the casing and selectively opening and closing the bypass pipe while moving between a first position and a second position according to a difference between an internal pressure of the casing and a pressure on a discharge side of the compression unit including a valve;
The second valve is
A valve space is provided, and a first hole communicating with the discharge side of the compression unit is formed on one side of the valve space, and a second hole communicating with the inner space of the casing is formed on the other side of the valve space, and the first 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 into the valve space of the valve housing and moving between the first and second positions according to a difference between the pressure supplied to the first hole and the pressure supplied to the second hole. high pressure compressor. According to claim 1,
The second valve blocks the bypass pipe when a compressive load is generated in the compression unit, while opening the bypass pipe when the compressive load is removed in the compression unit. delete According to claim 1,
A cross-sectional area of the second hole is greater than or equal to a cross-sectional area of the first hole. According to claim 1,
The third hole is formed in a direction crossing the center line of the first hole or the second hole,
The high pressure compressor, characterized in that 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. According to claim 1,
and the third hole is formed to be closed together at a position where the second hole is closed by the valve plate. According to claim 1,
A high-pressure compressor, characterized in that a valve spring for providing an elastic force to the valve plate is further provided at one side of the valve plate. 8. The method of claim 7,
The high-pressure compressor, characterized in that the valve spring is provided at the side of the second hole with the valve plate interposed therebetween. According to claim 1,
and the second valve is installed between the driving motor and the compression unit. 10. The method of claim 9,
A plurality of the discharge ports are provided so that the refrigerant compressed in the compression unit is discharged in both directions with respect to the axial direction based on the compression unit,
A plurality of refrigerant passages are formed through the compression unit so that the refrigerant discharged from one of the plurality of outlets is combined with the refrigerant discharged from the other outlet,
and the second valve is installed to communicate with any one refrigerant passage among the plurality of refrigerant passages. 11. The method of claim 10,
The high-pressure compressor, characterized in that the inner diameter of the refrigerant passage in which the second valve is installed among the plurality of refrigerant passages is greater than or equal to the inner diameter of the other refrigerant passages. 10. The method of claim 9,
The compression unit is provided with one discharge port so that the refrigerant compressed in the compression unit is discharged in one direction with respect to the axial direction,
The compression part is provided with a discharge cover for accommodating the discharge port,
The second valve is a high-pressure compressor, characterized in that provided in the discharge cover. a casing having an enclosed inner space;
a compression unit provided in the inner space of the casing, provided with a compression space for compressing the 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 open and close the discharge port according to a difference between the pressure of the inner space of the casing and the pressure of the compression space of the compression unit;
a discharge cover having a discharge space to accommodate the discharge valve;
a bypass pipe connecting the inner space of the casing and the suction side of the compression unit;
A first hole communicating with the discharge space of the discharge cover, a second hole communicating with the inner space of the casing, and a third hole communicating with the bypass pipe are provided, the first hole, the second hole, and the third hole a valve housing having a valve space in which all holes are communicated; and
The third position is provided movably in the valve space of the valve housing and moves between the first position and the second position according to a difference between the pressure supplied through the first hole and the pressure supplied through the second hole. A high-pressure compressor comprising a; a valve plate 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,
The valve housing is fixedly coupled to the middle of the bypass pipe from the outside of the casing,
At least one of the first hole and the second hole communicates with the inner space of the discharge cover or the inner space of the casing by a connection pipe passing through the casing. 14. The method of claim 13,
and a check valve for suppressing a reverse flow of the refrigerant discharged from the inner space of the casing into the inner space of the casing. compressor;
a condenser connected to the compressor;
a condenser fan provided on one side of the condenser;
an evaporator connected to the condenser; and
Including; an evaporator fan provided on one side of the evaporator;
The compressor is
A refrigeration cycle device comprising the high-pressure compressor of any one of claims 1, 2, and 4 to 16.

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