KR20070066294A - Refrigeration system - Google Patents

Abstract

A refrigeration system is provided to prevent lubrication oil from staying in a compression chamber, which is not in compression operation, thereby supplying refrigerant of high pressure smoothly. A refrigeration system includes a compressor(10) having a plurality of compression chambers(11,12), a condenser(40), a decompressing element(50) for decompressing refrigerant condensed by the condenser, an evaporator(60) for evaporating the decompressed refrigerant, and a refrigerant supply controller(80) for bypassing the refrigerant discharged from the compressor to the compressor for preventing oil from staying in the compression chambers. The refrigerant supply controller has a main bypass pipe(81) connected to a refrigerant discharge pipe(14) of the compressor, and a plurality of sub bypass pipes(82a,82b) connected to the main bypass pipe for guiding the refrigerant discharged from the compressor to the compression chambers, and a plurality of opening/closing valves such as solenoid valves(83a,83b) mounted to the sub bypass pipes correspondingly to the compression chambers for bypassing the refrigerant discharged from the compressor to the compression chamber not in compression operation, thereby supplying the refrigerant to the compression chamber selectively.

Description

Refrigeration system {Refrigeration system}

1 and 2 is a configuration diagram for explaining the configuration and operation of the refrigeration system according to a preferred embodiment of the present invention.

Figure 3 is a side cross-sectional view schematically showing a rotary compressor of the refrigeration system according to a preferred embodiment of the present invention.

 * Description of symbols on the main parts of the drawings *

 10 ... Rotary compressors 11, 12 ... 1,2 compression chamber

 14 Refrigerant discharge tube 20 Drive part

 23.Rotating shaft 30.Compression

 33, 34 ... first and second roller pistons 40 ... condenser

 50 ... decompression device 60 ... evaporator

 80 ... Refrigerant supply control unit 81 ... Main bypass tube

 82a, 82b ... 1,2 sub bypass pipe 83a, 83b ... 1,2 solenoid valve

 84 valve control unit 85 main refrigerant supply line

 86a, 86b ... 1,2 sub refrigerant supply pipe 87a, 87b ... 1,2 check valve

The present invention relates to a refrigeration system, and more particularly to a refrigeration system that can vary the operation performance by adjusting the flow amount of the refrigerant flowing in the system.

Generally, a refrigeration system is a device that induces a temperature change around a system by using a phase change and a temperature change of a refrigerant, and includes an air conditioner, a refrigerator, and a heat pump. The refrigeration system includes a compressor for compressing a refrigerant into a high temperature and high pressure gas refrigerant, a condenser for condensing the compressed gas refrigerant into a high pressure liquid refrigerant, a decompression device for reducing the condensed high pressure liquid refrigerant, and a low pressure liquid refrigerant. An evaporator for evaporating to a low pressure gas. These compressors, condensers, depressurizers and evaporators are piped to allow the refrigerant to circulate in a closed loop cycle.

Recently, refrigeration systems have been introduced to control the flow rate of the refrigerant flowing inside the system to vary the driving performance. This refrigeration system is especially applied to the air conditioner that harmonizes the indoor air to allow more precise control of the indoor temperature.

A refrigeration system that regulates the flow of refrigerant typically includes a variable displacement compressor having two compression chambers with different compression capacities, and selectively operates the two compression chambers of the variable displacement compressor to control the flow of refrigerant flowing through the system. Will be adjusted.

An example of a variable displacement compressor of such a refrigeration system is disclosed in US Patent US6860724 filed by the applicant.

The variable displacement compressor disclosed in US Patent US6860724 has a pair of compression chambers, a rotating shaft provided with a pair of eccentric parts that rotate eccentrically in each compression chamber, and combined with each eccentric part to compress in each compression chamber. A pair of roller pistons, a forward / reverse rotation motor for forward / reverse rotation of the rotating shaft, and a pair of cam bushes coupled to each roller piston to allow the roller pistons to eccentrically rotate or idle in accordance with the rotation direction of the rotation shaft. .

In the variable-capacity compressor having such a configuration, one roller piston is eccentrically rotated in the compression chamber in accordance with the rotational direction of the rotating shaft, and the other roller piston is idle in the compression chamber.

However, such a conventional variable displacement compressor has a problem in that the oil supplied to the compression chamber is lubricated in the compression chamber in which the compression action does not occur, thereby increasing the power consumption of the compressor, thereby reducing the overall efficiency of the refrigeration system. Have.

Therefore, various improvements have been proposed to solve this problem.

The present invention has been made in view of the above, it is possible to smoothly supply the high-pressure refrigerant to prevent the accumulation of oil for lubrication in the compression chamber is not a compression operation of the plurality of compression chambers provided in the variable capacity compressor The purpose is to provide a refrigeration system.

A refrigeration system according to the present invention for achieving the above object comprises a compressor having a plurality of compression chambers, a condenser for condensing the refrigerant compressed in the compressor, a decompression device for reducing the refrigerant condensed in the condenser, An evaporator for evaporating the refrigerant depressurized in the apparatus and a refrigerant supply control device for bypassing the refrigerant discharged from the compressor to the compressor to prevent oil from accumulating in the compression chambers.

The refrigerant control supply device includes a plurality of on / off valves corresponding to each of the compression chambers for bypassing and supplying the refrigerant discharged from the compressor to a compression chamber in which no compression action occurs.

Here, the plurality of open / close valves are solenoid valves, and the refrigerant supply control device may include a valve control device for controlling the opening and closing operations of the respective solenoid valves.

The refrigerant supply control device is connected to a main bypass pipe connected to a refrigerant discharge pipe through which refrigerant discharged from the compressor flows, and to the main bypass pipe to guide refrigerant discharged from the compressor to the compression chambers. It includes a plurality of sub bypass pipe, the plurality of sub bypass pipe may be installed one by one solenoid valve.

In addition, the refrigeration system according to the present invention, the main refrigerant supply pipe through which the refrigerant exiting the evaporator flows, and the main refrigerant supply pipe and each of the compression chamber to guide the refrigerant flowing into the main refrigerant supply pipe to the compressor. And a plurality of sub refrigerant supply pipes each of which is connected to each of the sub bypass pipes, and a plurality of backflow prevention devices installed in the sub refrigerant supply pipes to prevent the refrigerant flowing through the sub bypass pipes from flowing back into the main refrigerant supply pipe. The valve may further include.

Here, the plurality of non-return valves may be a check valve.

The compressor may be a rotary compressor provided with a plurality of roller pistons installed in each of the compression chambers to perform a compression action.

Hereinafter, a refrigeration system according to a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

1 and 2 is a configuration diagram for explaining the configuration and operation of the refrigeration system according to a preferred embodiment of the present invention, Figure 3 is a side cross-sectional view schematically showing a rotary compressor of the refrigeration system according to a preferred embodiment of the present invention. to be.

As shown in FIG. 1, a refrigeration system according to a preferred embodiment of the present invention includes a rotary compressor 10 for compressing a refrigerant at high temperature and high pressure, and a condenser 40 for condensing the refrigerant compressed in the rotary compressor 10. Bypasses the decompression device 50 for depressurizing the refrigerant condensed in the condenser 40, the evaporator 60 for evaporating the decompressed refrigerant in the decompression device 50, and the refrigerant discharged from the rotary compressor 10. It comprises a refrigerant supply control device 80 for selectively supplying to the rotary compressor (10).

The rotary compressor 10 has first and second compression chambers 11 and 12 having different compression capacities. The first compression chamber 11 is a high capacity compression chamber having a large compression capacity so that the refrigeration system can exhibit the maximum operating performance, and the second compression chamber 12 has an operation performance (eg, maximum operation) in which the refrigeration system is smaller than the maximum operating performance. It is a low capacity compression chamber which has a compression capacity smaller than the 1st compression chamber 11 so that 40% of performance may be exhibited.

As shown in FIG. 3, the rotary compressor 10 includes a cylindrical casing 13 forming a sealed exterior, a driving unit 20 and a compression unit 30 installed inside the casing 13.

The driving unit 20 is a stator 21 fixedly installed inside the casing 13 and a rotor 22 installed to rotate forward or reverse by electromagnetic interaction with the stator 21 at the center of the stator 21. And a rotating shaft 23 fixedly installed at the center of the rotor 22 and rotating together with the rotor 22. The lower end of the rotation shaft 23 is provided with a weight balance 24 for reducing the vibration caused by the imbalance of the center of rotation.

The compression unit 30 includes first and second eccentric portions 31 and 32 provided on the rotating shaft 23 and first and second rollers coupled to the first and second eccentric portions 31 and 32. First and second compression chambers 11 and 12 in which the refrigerant is compressed by the operation of the pistons 33 and 34, the first and second roller pistons 33 and 34, and the first eccentric portion The first cam bush 35 provided between the 31 and the first roller piston 33, and the second cam bush 36 provided between the second eccentric portion 32 and the second roller piston 34. It includes.

The first cam bush 35 causes the first roller piston 33 to eccentrically rotate with respect to the rotation shaft 23 when the rotation shaft 23 is rotated forward, and the first roller piston 33 when the rotation shaft 23 is reversely rotated. The center of rotation of the coincides with the center of rotation of the rotating shaft 23. On the contrary, the second cam bush 36 causes the rotational center of the first roller piston 33 to coincide with the rotational center of the rotational shaft 23 when the rotational axis 23 rotates forward, and when the rotational axis 23 is reversed. The second roller piston 34 makes the eccentric rotation about the rotation shaft 23.

Therefore, when the rotating shaft 23 rotates forward, the first roller piston 33 compresses the refrigerant introduced into the first compression chamber 11 while eccentrically rotating in the first compression chamber 11, while the second roller piston is rotated. 34 is idle in the second compression chamber 12 so as not to compress the refrigerant in the second compression chamber 12. On the contrary, when the rotating shaft 23 rotates in reverse, the second roller piston 34 compresses the refrigerant in the second compression chamber 12 while eccentrically rotating in the second compression chamber 12, and the first roller piston 33 ) Is idle in the first compression chamber (11). Thus, the refrigerant compressed in the first compression chamber 11 or the second compression chamber 12 is discharged to the outside through the refrigerant discharge pipe 14 provided on the casing 13.

The lower portion of the casing 13 is provided with an oil pan 15 for storing oil O for lubricating the friction generating portion.

The rotary compressor 10 having such a configuration is the same as the compressor disclosed in the US patent US6860724 filed by the present applicant, the description of the detailed configuration and operation thereof will be omitted.

The condenser 40 is connected to the rotary compressor 10 through the refrigerant discharge pipe 14 and condenses the high temperature and high pressure gas refrigerant discharged from the rotary compressor 10 into a liquid refrigerant of room temperature and high pressure. A blower 45 is installed near the condenser 40, and the blower 45 forcibly blows air around the condenser 40 so that the high temperature and high pressure refrigerant flowing into the condenser 40 smoothly exchanges heat with the surrounding air. It helps to dissipate heat to the outside smoothly.

The decompression device 50 is connected to the condenser 40 and the evaporator 60 through a pipe, and decompresses the refrigerant at room temperature and high pressure condensed in the condenser 40 to make it easy to evaporate in the evaporator 60.

The evaporator 60 evaporates the liquid refrigerant depressurized by the decompression device 50 into a gas refrigerant of low temperature and low pressure. The refrigerant takes heat around the evaporator 60 and cools it around the evaporator 60 while evaporating. Near the evaporator 60, a blower 65 is installed to help heat exchange of the refrigerant passing through the evaporator 60 by forcibly blowing air around the evaporator 60.

The refrigerant passing through the evaporator 60 is transferred to the accumulator 70, and the accumulator 70 is installed between the evaporator 60 and the rotary compressor 10 so that only vaporized refrigerant may be introduced into the rotary compressor 10. do. That is, the accumulator 70 separates the liquid refrigerant and the gaseous refrigerant from the refrigerant passing through the evaporator 60, and passes only the gaseous refrigerant toward the rotary compressor 10.

The refrigerant supply control device 80 controls the flow of the refrigerant supplied to the first and second compression chambers 11 and 12 of the rotary compressor 10, respectively. The refrigerant supply control device 80 includes a main bypass pipe 81, first and second sub bypass pipes 82a and 82b, first and second solenoid valves 83a and 83b, and a valve. The control device 84, the main refrigerant supply pipe 85, first and second sub refrigerant supply pipes 86a and 86b, and first and second check valves 87a and 87b are included.

The main bypass pipe 81 is connected to the refrigerant discharge pipe 14 to bypass the high temperature and high pressure gas refrigerant discharged from the rotary compressor 10. The first and second sub bypass pipes 82a and 82b are connected in parallel to the main bypass pipe 81. A first solenoid valve 83a is provided in the first sub bypass pipe 82a, and a second solenoid valve 83b is provided in the second sub bypass pipe 82b. The first and second solenoid valves 83a and 83b are selectively opened and closed by the valve control device 84, and the refrigerant flows into the first sub bypass pipe 82a and the second sub bypass pipe 82b. To control the flow.

The main refrigerant supply pipe 85 guides the refrigerant passing through the accumulator 70 toward the rotary compressor 10. The first and second sub refrigerant supply pipes 86a and 86b are connected in parallel to the main refrigerant supply pipe 85. A first check valve 87a is installed in the first sub refrigerant supply pipe 86a and a second check valve 87b is installed in the second sub refrigerant supply pipe 86b.

A first sub bypass pipe 82a is connected to the first sub refrigerant supply pipe 86a, and a connection position of the first sub bypass pipe 82a is between the first check valve 87a and the rotary compressor 10. do. In addition, a second sub bypass pipe 82b is connected to the second sub refrigerant supply pipe 86b, and a connection position thereof is between the second check valve 87b and the rotary compressor 10. In this way, a first check valve 87a is positioned between the first sub bypass pipe 82a and the main refrigerant supply pipe 85 to restrict the flow direction of the refrigerant, and the second sub bypass pipe 82b and the main refrigerant. The second check valve 87b is positioned between the supply pipes 85 to restrict the flow direction of the refrigerant, so that the high-pressure refrigerant flowing along the first and second sub bypass pipes 82a and 82b receives the main refrigerant supply pipe. Will not flow back to (85).

Hereinafter, with reference to the accompanying drawings will be described the operation of the refrigeration system according to a preferred embodiment of the present invention.

1 illustrates a case in which a refrigerating system exhibits maximum operating performance while a compression action occurs in the first compression chamber 11 having a large compression capacity. At this time, the rotary shaft 23 of the rotary compressor 10 rotates forward. When the rotating shaft 23 rotates forward, as shown in FIG. 3, the first roller piston 33 is eccentrically rotated in the first compression chamber 11 by the action of the first cam bush 35, thereby compressing the first compression. The refrigerant supplied into the chamber 11 is compressed. On the other hand, the center of rotation of the second roller piston 34 of the second compression chamber 12 coincides with the center of rotation of the rotation shaft 23 by the action of the second cam bush 36.

When the refrigerant is compressed in the first compression chamber 11 of the rotary compressor 10, the valve control device 84 closes the first solenoid valve 83a and opens the second solenoid valve 83b to open the first sub-by. The refrigerant may not flow to the pass pipe 82a and the refrigerant may flow to the second sub bypass pipe 82b.

As shown in FIG. 1, the refrigerant compressed in the first compression chamber 11 is discharged to the outside of the rotary compressor 10 through the refrigerant discharge pipe 14 to condenser 40, the pressure reducing device 50, and the evaporator. It passes through 60 and the accumulator 70 in order. The gas refrigerant passing through the accumulator 70 flows along the main refrigerant supply pipe 85 and branches from the first and second sub refrigerant supply pipes 86a and 86b to allow the first and second check valves 87a and 87b to flow. Passes through the first and second compression chamber (11, 12) of the rotary compressor (10).

Meanwhile, some of the high temperature and high pressure refrigerant discharged to the refrigerant discharge pipe 14 flows to the main bypass pipe 81. The refrigerant flowing into the main bypass pipe 81 continuously flows along the second sub bypass pipe 82b in which an internal flow path is opened, and then flows into the second sub coolant supply pipe 86b to supply the second sub refrigerant supply pipe. It flows into the 2nd compression chamber 12 of the rotary compressor 10 through 86b. When the refrigerant flows into the second sub refrigerant supply pipe 86b from the second sub bypass pipe 82b, the second check valve 87b prevents the refrigerant from flowing back toward the main refrigerant supply pipe 85 and prevents the second compression chamber ( 12) Only flow toward the side.

The high temperature and high pressure refrigerant introduced into the second compression chamber 12 through the second sub refrigerant supply pipe 86b together with the low temperature low pressure refrigerant flowing along the main refrigerant supply pipe 85 is charged in the second compression chamber 12. The oil O supplied from the oil pan 15 (see FIG. 3) to the second compression chamber 12 is prevented from accumulating.

On the contrary, when the rotary shaft 23 of the rotary compressor 10 reversely rotates, the refrigerant is compressed in the second compression chamber 12 and the refrigeration system has a driving performance smaller than the maximum operating performance (for example, 40 of the maximum operating performance). %). When the rotating shaft 23 rotates in reverse, the first roller piston 33 is idling by the first cam bush 35 so that the center of rotation coincides with the center of rotation of the rotating shaft 23 in the first compression chamber 11. The second roller piston 34 compresses the refrigerant supplied to the second compression chamber 12 while eccentrically rotating by the action of the second cam bush 36.

As shown in FIG. 2, the high temperature and high pressure refrigerant compressed in the second compression chamber 12 is discharged through the refrigerant discharge pipe 14 to condenser 40, the pressure reducing device 50, the evaporator 60, and the accumulator. It passes through 70 in order to flow to the main refrigerant supply pipe (85). The refrigerant flowing into the main refrigerant supply pipe 85 is branched into the first and second sub refrigerant supply pipes 86a and 86b and passes through the first and second check valves 87a and 87b, respectively. It flows into the compression chamber 11 (12).

As such, while the refrigerant circulates while forming a refrigeration cycle, some of the high temperature and high pressure refrigerant discharged to the refrigerant discharge pipe 14 flows to the main bypass pipe 81. Since the first solenoid valve 83a is opened and the second solenoid valve 83b is closed by the valve control device 84 while the compression action occurs in the second compression chamber 12, it follows the main bypass pipe 81. As shown in FIG. The flowing refrigerant continues to flow along the first sub bypass pipe 82a.

The high temperature, high pressure refrigerant flowing along the first sub bypass pipe 82a flows into the first sub refrigerant supply pipe 86a. In addition, the high temperature and high pressure refrigerant flowing into the first sub refrigerant supply pipe 86a does not flow back toward the main refrigerant supply pipe 85 due to the first check valve 87a and flows along the main refrigerant supply pipe 85. Together with the first compression chamber (11). The refrigerant introduced into the first compression chamber 11 is filled in the first compression chamber 11 while preventing the oil O rising from the oil pan 15 (see FIG. 3) from accumulating in the first compression chamber 11. do.

According to the present invention, by using the solenoid valve for selectively opening and closing the flow path of the refrigerant and the check valve to prevent the reverse flow of the refrigerant it is possible to smoothly supply the compressed high temperature and high pressure refrigerant to the compression chamber without the compression action. . Therefore, it is possible to prevent oil from accumulating in the compression chamber, and to increase the power consumption of the rotary compressor and to reduce the efficiency of the refrigeration system.

The present invention described above is not limited to the configuration and operation as illustrated and described. That is, the present invention is capable of various changes and modifications within the spirit and scope of the appended claims.

Claims (11)

A refrigeration system having a compressor having a plurality of compression chambers, a condenser for condensing the refrigerant compressed by the compressor, a decompression device for depressurizing the refrigerant condensed in the condenser, and an evaporator for evaporating the decompressed refrigerant in the decompression device. In And a refrigerant supply control device having a plurality of on / off valves corresponding to each of the compression chambers for bypassing and supplying the refrigerant discharged from the compressor to a compression chamber in which no compression action occurs. Refrigeration system. The method of claim 1, And the plurality of on / off valves are solenoid valves, and the refrigerant supply control device includes a valve control device for controlling opening and closing operations of the respective solenoid valves. The method of claim 2, The refrigerant supply control device may be connected to a main bypass pipe connected to a refrigerant discharge pipe through which refrigerant discharged from the compressor flows, and to the main bypass pipe for guiding refrigerant discharged from the compressor to the compression chambers. A refrigeration system, characterized in that it comprises a plurality of sub-bypass pipe is installed one by one solenoid valve. The method of claim 3, wherein The main refrigerant supply pipe through which the refrigerant exiting the evaporator flows, and the main refrigerant supply pipe and the respective compression chambers are connected to guide the refrigerant flowing into the main refrigerant supply pipe to the compressor, and the sub bypass pipes are connected one by one. And a plurality of non-return valves installed in the sub refrigerant supply pipes such that the plurality of sub refrigerant supply pipes and the refrigerant flowing through the sub bypass pipes do not flow back into the main refrigerant supply pipes. system. The method of claim 4, wherein And said plurality of non-return valves are check valves. The method of claim 1, The compressor is a refrigeration system, characterized in that the rotary compressor is provided in each of the compression chamber is provided with a plurality of roller pistons for a compression action. A compressor having a plurality of compression chambers, a condenser for condensing the refrigerant discharged to the refrigerant discharge tube coupled to the compressor, a decompression device for depressurizing the refrigerant condensed in the condenser, and a refrigerant depressurized in the decompression device. In refrigeration systems with an evaporator, A main bypass pipe connected to the refrigerant discharge pipe, a plurality of sub bypass pipes connected to the main bypass pipe to guide refrigerant flowing through the main bypass pipe to the compression chambers, and the main bypass pipe. And a refrigerant supply control device further comprising an on / off valve installed between the main bypass pipe and the plurality of compression chambers to supply the refrigerant flowing through the pass pipe to the compression chamber in which the compression action does not occur among the plurality of compression chambers. Refrigeration system comprising a. The method of claim 7, wherein The on-off valve is composed of a plurality of solenoid valves installed in each of the sub bypass pipe, the refrigerant supply control device further comprises a valve control device for controlling the opening and closing operation of each of the solenoid valves system. The method of claim 8, The main refrigerant supply pipe through which the refrigerant exiting the evaporator flows, and the main refrigerant supply pipe and the respective compression chambers are connected to guide the refrigerant flowing into the main refrigerant supply pipe to the compressor, and the sub bypass pipes are connected one by one. And a plurality of non-return valves installed in the sub refrigerant supply pipes such that the plurality of sub refrigerant supply pipes and the refrigerant flowing through the sub bypass pipes do not flow back into the main refrigerant supply pipes. system. The method of claim 9, And said plurality of non-return valves are check valves. The method of claim 7, wherein The compressor is a refrigeration system, characterized in that the rotary compressor is provided in each of the compression chamber is provided with a plurality of roller pistons for a compression action.

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