KR100853357B1 - Pressure Balancer of Air Conditioner with Multiple Compressors - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner using a plurality of compressors. In particular, when one or all the compressors are stopped, the pressure equalization time of the stopped compressor is shortened, and the refrigerant and oil discharged from the running compressor are accumulated in the stopped compressor. A pressure equalizer of an air conditioner having a plurality of compressors, the first and second compressors for compressing and discharging a refrigerant; A condenser connected to each of the conduits connected to the first and second compressors by lamination; An expansion valve connected to the condenser; An evaporator connected to the expansion valve; A common receiver connected to the evaporator; And first and second accumulators connected to the common receiver and the outlet parts connected to the first and second compressors, respectively, and the first and second flows to which the first and second compressors, the common receiver, and the first and second accumulators are connected, respectively. The change means is configured, and by using the flow change means, the pressure equilibrium time of the stopped compressor can be shortened to reduce the time to restart the stopped compressor according to the change of the room temperature. When the change means is operated, the refrigerant and oil discharged from the compressor in operation are completely blocked so as not to flow into the stationary compressor, thereby preventing the accumulation of unnecessary refrigerant and oil.

Description

Pressure balanced equipment in air conditioner with multi compressors

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner using a plurality of compressors. In particular, when one or all the compressors are stopped, the pressure equalization time of the stopped compressor is shortened, and the refrigerant and oil discharged from the running compressor are accumulated in the stopped compressor. To a pressure balancer of an air conditioner having a plurality of compressors.

In general, an air conditioner includes a compressor for compressing a refrigerant at a high temperature and a high pressure, a condenser for isothermal condensing the refrigerant by heat exchange with outside air, an expansion valve which is an expansion device for adiabatic expansion of the condensed refrigerant, and an expanded refrigerant into a tube. It is composed of an evaporator for isothermal evaporation by heat exchange with indoor air.

At this time, in order to reduce the waste of energy efficiency, two compressors having different compression capacities, each of which can be operated independently according to indoor load conditions, are installed.

1 is a configuration diagram of an air conditioner using two conventional compressors.

As shown in Fig. 1, two compressors 1 and 2, a condenser 4 for condensing the compressed refrigerant, an expansion valve 5 for expanding the refrigerant, and an evaporator 6 for evaporating the refrigerant, In addition, the non-return check valves 15 and 16 which prevent the refrigerant formed at high temperature and high pressure through the compressors 1 and 2 from flowing back to the compressors 1 and 2 are provided. It is installed on the discharge part side.

In addition, an oil separator 3 is installed between the condenser 4 and the compressors 1 and 2 to prevent the oil from flowing into the refrigeration cycle, and the oil separated from the oil separator 3 is an oil recovery pipe ( It enters into the suction part of the compressor (1, 2) through 9,10. In addition, accumulators 7 and 8 are respectively provided in the suction unit. Here, the accumulators 7 and 8 store the excess refrigerant generated during the refrigerating cycle, and at the same time, supply the oil proportional to the refrigerant intake of the compressors 1 and 2.

During the cooling operation, the high-temperature and high-pressure refrigerant from the compressors 1 and 2 located at the outdoor side is sent to the condenser 4 to condense, and then expanded to the low-temperature and low-pressure refrigerant at the expansion valve 5, and then sent to the evaporator 6. At this time, the evaporator 6 located at the indoor side absorbs heat from the indoor side and discharges cold air, and the refrigerant is sent to the accumulators 7 and 8 at the outdoor side and then sent to the compressors 1 and 2 and compressed. To perform the cooling function.

When two compressors are operated at the same time and reach the set room temperature, one of the compressors stops and the other compressors continue to operate to maintain the room temperature. At this time, the stationary compressor maintains high pressure due to the compressed high-pressure refrigerant, and the suction part of the stationary compressor is maintained before the refrigerant is compressed, so that the low pressure is maintained. In a stationary compressor, the high pressure refrigerant moves to the low pressure inlet to achieve pressure balance.

At this time, when the pressure of the stationary compressor is balanced, the stationary compressor is restarted. The time required for the stationary compressor to reach the pressure equilibrium is considerably long in several minutes to several tens of minutes, and it varies depending on the capacity of the compressor and the system operating conditions. Therefore, the stationary compressor cannot be operated until the pressure equilibrium is reached, and thus, the compressor that is suitable for the compression capacity is not immediately operated due to the change of the room temperature. In addition, the time to reach the pressure balance depends on the system operating conditions and the compressor capacity. Therefore, the actual system design takes into account sufficient safety time, and in this case, the compressor is kept at a standstill despite the pressure balance. In order to solve the above problems, power consumption is increased by stopping and restarting all compressors.

In addition, when one of the compressors is stopped, oil discharged from the running compressor flows into the accumulator of the stopped compressor and accumulates in the accumulator until restarting. This causes oil shortage of the compressor to operate. To prevent this, two compressors must be operated simultaneously to achieve oil balance. When two compressors are operated simultaneously, power consumption increases and system efficiency decreases.

The present invention has been made to solve the above problems, and an object of the present invention is to shorten the pressure equilibrium time between the discharge part and the suction part of the stationary compressor by installing a flow change means at the upper ends of the two pressure devices.

In addition, it is another object to form a stationary compressor as an independent system to prevent the refrigerant and oil discharged from the running compressor to flow into the stationary compressor.

As a means for achieving the above object,

First and second compressors for compressing and discharging the refrigerant; A condenser connected to each of the conduits connected to the first and second compressors by lamination; An expansion valve connected to the condenser; An evaporator connected to the expansion valve; A common receiver connected to the evaporator; And first and second accumulators connected to the common receiver and the outlet parts connected to the first and second compressors, respectively, and the first and second flows to which the first and second compressors, the common receiver, and the first and second accumulators are connected, respectively. Characterized by the change means

In addition, the first and second flow changing means is characterized in that the four-way valve.

In addition, the refrigerant discharged from the first compressor is output through the first inlet of the first flow changing means to the first outlet, and the refrigerant discharged from the common receiver is output to the second outlet through the second inlet of the first flow changing means. And is sucked into the first accumulator.

In addition, the refrigerant discharged from the second compressor is output to the first outlet through the second inlet of the second flow changing means, and the refrigerant discharged from the common receiver is output to the second outlet through the first inlet of the second flow changing means. And is sucked into the second accumulator.

In addition, when the first and second compressors are operated at the same time, any one first compressor and the first inlet and the first outlet of the first flow changing means connected to the first compressor are connected by one conduit, and the other second compressor is And the second inlet and the first outlet of the second flow changing means connected to each other by one pipe, and the refrigerant discharged from each of the first outlets is laminated and supplied to the condenser.

In addition, when any one of the compressors of the first and second compressors is stopped, the refrigerant of the first compressor in operation is supplied to the condenser via the first flow change means, and the refrigerant of the stopped second compressor is supplied to the second compressor. The pressure balance may be achieved by circulating the second inlet and the second outlet of the flow changing means to the second compressor stationary through the second accumulator.

In addition, a check valve is further included in each conduit connected to the first and second flow changing means in the common receiver.

In addition, the second flow changing means connected to the stationary second compressor is operated with the same electrical signal as the electrical signal for stopping the second compressor, and the stopped second compressor is operated by the refrigerant backflow prevention function of the second flow changing means. It is characterized by forming a separate system by blocking the refrigerant flow to the second compressor.

Other objects, specific advantages and novel features of the present invention will become more apparent from the following detailed description and the preferred embodiments associated with the accompanying drawings.

As described above, according to the present invention, it is possible to shorten the pressure balancing time of the stopped compressor by using the flow changing means, thereby reducing the time for restarting the stopped compressor in accordance with the change of the room temperature.

In addition, since the flow changing means is operated with the same electrical signal as when the compressor is stopped, there is no need to install a new control unit for controlling the flow changing means.

In addition, when restarting the stopped compressor, the flow change means is operated using the compressor without a separate electrical signal, so even if the stop / standby time of the stopped compressor becomes long, restart of the compressor and the flow change means is desired.

In addition, when the flow change means installed in the stationary compressor is operated, the refrigerant and oil discharged from the compressor in operation are completely blocked so as not to flow into the stationary compressor, thereby preventing the accumulation of unnecessary refrigerant and oil.

Although the present invention has been described in connection with the above-mentioned preferred embodiments, various other modifications and variations may be made without departing from the spirit and scope of the invention. Accordingly, it is intended that the appended claims cover such modifications and variations as fall within the true scope of the invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. First, in adding reference numerals to components of each drawing, the same reference numerals are used for the same components as much as possible even if they are shown in different drawings. In addition, in the following description of the present invention, if it is determined that a detailed description of a related known function or configuration may unnecessarily obscure the subject matter of the present invention, the detailed description thereof will be omitted.

2 is a flow chart of a refrigerant of an air conditioner when two compressors are normally operated according to a preferred embodiment of the present invention.

2, the first and second compressors (10a, 10b) for compressing and discharging the refrigerant; A condenser 30 to which respective pipes connected to the first and second compressors 10a and 10b are laminated and connected; An expansion valve 40 connected to the condenser 30; An evaporator 50 connected to the expansion valve 40; A common receiver 60 connected to the evaporator 50; And first and second accumulators 80a and 80b connected to the common receiver 60 and connected to the first and second compressors 10a and 10b, respectively, and having first and second compressors 10a and 10b. ) And first and second flow changing means 20 and 25 connected to the common receiver 60 and the first and second accumulators 80a and 80b, respectively.

The first and second flow changing means 20, 25 use a four way valve.

The high pressure refrigerant discharged from the first and second compressors 10a and 10b is passed to the condenser 30 through the first and second flow changing means 20 and 25 connected to the first and second compressors 10a and 10b, respectively. Condensation. The condensed refrigerant passes through the expansion valve 40 and is evaporated through the evaporator 50, and the refrigerant having undergone heat exchange is again passed through the common receiver 60 and the first and second flow changing means 20 and 25. After accumulating in the accumulators 80a and 80b, the process of supplying them to the first and second compressors 10a and 10b is repeated.

Either one of the first and second compressors 10a and 10b is driven or simultaneously driven. In addition, the refrigerant is circulated by repeating the above process.

Hereinafter, a description will be given of an embodiment of the present invention.

As shown in FIG. 2, when the compressors 10a and 10b are operated at the same time, the first inlet 20b and the first outlet 20a of the first compressor 10a and the first flow changing means 20 are closed. It is connected by one pipeline, and the second inlet 25d of the second compressor 10b and the second flow changing means 25 and the first outlet 25a are connected by one pipeline. The first discharge pipe 11 and the second discharge pipe 12 connected to each of the first outlets 20a and 25a are laminated by the connecting pipe 14 and connected to the condenser 30.

That is, the high pressure refrigerant discharged from the first compressor 10a is input to the first inlet 20b of the first flow changing means 20 and output to the first outlet 20a. The high pressure refrigerant discharged from the second compressor 10b is input to the second inlet 25d of the second flow changing means 25 and output to the first outlet 25a.

The refrigerant condensed in the condenser 30 generates cold air while passing through the expander 40 and the evaporator 50 in sequence, and the low pressure refrigerant passing through the evaporator 50 is a common receiver 60 connected to the evaporator 50. Gathered in).

The refrigerant collected in the common receiver 60 is input to the second inlet 20d of the first flow changing means 20, is supplied to the first accumulator 80a through the second outlet 20c, and the second flow changing means. It is input to the 1st inlet 25b of (25), and is supplied to the 2nd accumulator 80b through the 2nd outlet 25c, respectively.

The first and second accumulators 80a and 80b store surplus refrigerant generated according to the operating capacities of the first and second compressors 10a and 10b.

The refrigerant supplied to the first and second accumulators 80a and 80b is sucked into the first and second compressors 10a and 10b, respectively, and the above process is repeated, and the refrigerant circulates.

3 is a flow chart of a refrigerant of an air conditioner when one compressor is operated according to a preferred embodiment of the present invention. In the present invention, a case where the second compressor 10b (compressor 10b shown on the right side of FIG. 3) is stopped will be described.

As shown in FIG. 3, when two compressors are operated at the same time and reach the set room temperature, one compressor is stopped and the other compressor is continuously operated to maintain the room temperature.

When the second compressor 10b is stopped, the high-pressure refrigerant discharged from the first compressor 10a passes through the first discharge pipe 11 along the connecting pipe 14 to the condenser 30, the expansion valve 40, and the evaporator. The circuit circulates normally while passing through the 50 and the common receiver 60.

The refrigerant of the first compressor 10a in operation is supplied to the condenser 30 through the first inlet 20b and the first outlet 20a of the first flow changing means 20 constituted by one pipe. The high pressure refrigerant discharged from the first compressor 10a passes through the connecting pipe 14 through the first discharge pipe 11, but the second compressor 10b is stopped, so the high pressure refrigerant is discharged from the second discharge pipe ( 12. The first compressor 10a in operation has the same refrigerant flow as when the two compressors are operating, as shown in FIG.

Since the first and second flow changing means 20 and 25 of the present invention include a function of preventing backflow of the refrigerant, the refrigerant moved to the second discharge pipe 12 passes through the second flow changing means 25. can not do.

On the other hand, when the second compressor 10b reaches a constant room temperature and stops as shown in FIG. 3, the second flow changing means 25 simultaneously outputs an electrical signal generated when the second compressor 10b is stopped. It works. That is, the first inlet 25b of the second flow changing means 25 and the first outlet 20a are connected by one pipeline, and the stopped second compressor 10b is a refrigerant flow of the first compressor 10a. Because it is blocked, it is formed as an independent system.

The stopped second compressor 10b is maintained at a high pressure due to the compressed high-pressure refrigerant, and the suction portion of the stopped second compressor 10b is at a low pressure before the refrigerant is compressed. A pressure difference of) is generated. Therefore, the stationary second compressor 10b is moved to the suction portion of the low pressure through the second flow changing means 25 to achieve the pressure balance.

That is, the high-pressure refrigerant is supplied to the second accumulator 80b through a pipe connecting the second inlet 25d and the second outlet 25c of the second flow changing means 25 to the second compressor 10b. Is inhaled. Through the above process, the pressure balance of the stopped second compressor 10b is achieved.

Therefore, unlike the conventional air conditioner, the stationary second compressor 10b is operated by the second flow changing means 25 to form an independent system, so that the pressure difference between the stationary second compressor 10b is quickly balanced, By shortening the time to reach the pressure equilibrium, it is possible to reduce the time for restarting the second compressor 10b that is stopped according to the change in the room temperature.

In addition, when the second compressor 10b, which forms an independent system by the second flow changing means 25, is operated again, the second flow changing means 25 prevents the backflow of the refrigerant, so that the second compressor 10b normally operates. Can be driven.

In addition, since the stopped second compressor 10b is formed as an independent system, the refrigerant and oil discharged from the first compressor 10a in operation can be prevented from accumulating in the stopped second compressor 10b. That is, the first and second flow changing means 20, 25 prevent the refrigerant and oil of the compressor which is operated from accumulating in the stationary compressor.

In the present invention, the flow of the refrigerant at the time of stopping the second compressor 10b has been described. However, the compressor stopped at the same time as described above may be formed as an independent system even when the other compressor is stopped.

In addition, even when two or more compressors are used, an air conditioner may be configured by using a flow changing means as in the correct embodiment of the present invention.

In addition, the first and second flow changing means (20, 25) prevents the high-pressure refrigerant discharged from the operating first compressor (10a) and oil flow back into the stationary second compressor (10b), but common The first and second check valves 70a and 70b are further installed in a conduit to which the second inlet 20d and the first inlet 25b of the receiver 60 and the first and second flow changing means 20 and 25 are respectively connected. This can completely block backflow of refrigerant and oil.

1 is a configuration diagram of an air conditioner using two conventional compressors.

2 is a refrigerant flow diagram of an air conditioner when two compressors are normally operated according to a preferred embodiment of the present invention.

3 is a flow chart of a refrigerant of an air conditioner during operation of one compressor according to a preferred embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

10a, 10b: compressor 20, 25: first and second flow changing means

11: 1st discharge pipe 12: 2nd discharge pipe

14: connector 20a, 25a: first exit

20b, 25b: first entrance 20c, 25c: second exit

20d, 25d: second inlet 30: condenser

40 expansion valve 50 evaporator

60: common receiver 70a, 70b: 1st, 2nd check valve

80a, 80b: 1st, 2nd accumulator

Claims (8)

First and second compressors 10a and 10b for compressing and discharging the refrigerant; A condenser 30 to which respective pipes connected to the first and second compressors 10a and 10b are laminated and connected; An expansion valve 40 connected to the condenser 30; An evaporator (50) connected to the expansion valve (40); A common receiver 60 connected to the evaporator 50; And An inlet part is connected to the common receiver 60, and the outlet part is composed of first and second accumulators 80a and 80b connected to the first and second compressors 10a and 10b, respectively. The first and second compressors 10a and 10b, the common receiver 60 and the first and second accumulators 80a and 80b are connected to the first and second flow changing means 20 and 25, respectively. Pressure equalizer of an air conditioner having a plurality of compressors. The method of claim 1, The first and second flow changing means (20, 25) is a pressure equalizer of the air conditioner having a plurality of compressors, characterized in that the four-way valve. The method of claim 1, The refrigerant discharged from the first compressor (10a) is output through the first inlet (20b) of the first flow change means 20 to the first outlet (20a), the refrigerant discharged from the common receiver 60 The air conditioner having a plurality of compressors is characterized in that the output through the second inlet (20d) of the first flow change means 20 is output to the second outlet (20c) and sucked into the first accumulator (80a) Pressure equalizer. The method of claim 1, The refrigerant discharged from the second compressor (10b) is output to the first outlet (25a) through the second inlet (25d) of the second flow change means 25, the refrigerant discharged from the common receiver 60 Is passed through the first inlet 25b of the second flow changing means 25 and is output to the second outlet 25c and sucked into the second accumulator 80b. Pressure equalizer. The method of claim 1, When the first and second compressors 10a and 10b are operated at the same time, any one of the first compressor 10a and the first inlet 20b of the flow changing means 20 connected to the first compressor 10a and The first outlet 20a is connected by one pipeline, and the remaining second compressor 10b and the second inlet 25d and the first outlet 25a of the second flow changing means 25 connected thereto are one pipeline. The pressure balancer of the air conditioner having a plurality of compressors, characterized in that the refrigerant is discharged from each of the first outlet (20a, 25a) is connected to the condenser (30). The method of claim 1, When any one of the first and second compressors 10a and 10b is stopped, the refrigerant of the first compressor 10a in operation is transferred to the condenser 30 via the first flow changing means 20. The supplied and stopped refrigerant of the second compressor (10b) is a second accumulator (via the conduit connecting the second inlet 25d and the second outlet 25c of the second flow change means 25) Pressure equalization device of the air conditioner having a plurality of compressors, characterized in that the pressure balance is made by the process circulated to the second compressor (10b) stopped through 80b). The method of claim 1, A plurality of compressors, characterized in that the first and second check valve (70a, 70b) is further included in each of the pipelines connected to the first and second flow changing means (20, 25) in the common receiver (60) Pressure equalizer of air conditioner having. The method of claim 6, The second flow changing means 25 connected to the stationary second compressor 10b is operated with the same electrical signal as the electrical signal for stopping the second compressor 10b to change the second flow compressor 10b that is stopped. An air conditioner having a plurality of compressors, characterized in that the refrigerant flow of the means 25 prevents the refrigerant flow of the first compressor 10a from going to the second compressor 10b. Pressure equalizer.

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