KR100569780B1 - One body type air cooled unit adopting evaporation temperature changeableness method for heat pump device - Google Patents

Abstract

The present invention uses the infinite air heat source of the atmosphere, but absorbs the low-temperature air heat source or high-temperature air heat source in accordance with the environment changes during the summer and summer, and the evaporation temperature, the heat transfer area and the air flow rate of the refrigerant variable and stable operation of the heat pump device An evaporation temperature variable integrated air cooled evaporator device for a heat pump device that maximizes good performance and energy efficiency.

The evaporation temperature variable integrated air-cooled evaporator of the heat pump device of the present invention absorbs the surrounding air heat source and evaporates the refrigerant, and is connected in parallel and has two evaporators 10a and 10b having a predetermined capacity. 10a, 10b, blowers 20a and 20b for inducing the flow of air, and high-temperature electronic valves 30a respectively installed on the refrigerant inlet pipe 40a for introducing refrigerant into the evaporator 10a. And a low-temperature electronic valve 30b and a low-temperature expansion valve 31b and the high-temperature expansion valve 31 which are respectively installed in order on the high-temperature expansion valve 31a and the refrigerant inlet pipe 40b for introducing the refrigerant to the evaporator 10b. (31a) a connection pipe 40c for connecting between the refrigerant inlet pipe 40a downstream and the refrigerant inlet pipe 40b downstream of the low-temperature expansion valve 31b, and the refrigerant being installed on the connection pipe 40c. To flow only from the inlet pipe 40a to the refrigerant inlet pipe 40b. Is characterized in that it comprises a reverse side 31c.

Heat pump, air-cooled evaporator, evaporation temperature, variable type, integrated type, one side suction type, both side suction type, high temperature expansion valve, low temperature expansion valve, reverse valve, electronic valve, liquid separator

Description

One body type air cooled unit adopting evaporation temperature changeableness method for heat pump device}

Figure 1a is a block diagram of a high temperature evaporation state of the one-side suction type evaporator as an embodiment of the evaporation temperature variable integral air cooled evaporator for a heat pump device according to the present invention,

1B is a configuration diagram of a low-temperature evaporation state of a one-side suction type evaporator as an embodiment of the evaporation temperature variable integrated air-cooled evaporator for a heat pump device according to the present invention;

Figure 2a is a configuration diagram of a high temperature evaporation state of the two-side suction type evaporator as another embodiment of the evaporation temperature variable integral air cooled evaporator for a heat pump device according to the present invention,

Figure 2b is a configuration diagram of a low-temperature evaporation state of the two-side suction type evaporator as another embodiment of the evaporation temperature variable integral air cooled evaporator for a heat pump device according to the present invention,

3A is a refrigerant system diagram of a high temperature evaporation state of a heat pump apparatus employing a one-side suction type air-cooled evaporator according to the present invention;

3b is a refrigerant system diagram of a low temperature evaporation state of a heat pump apparatus employing a one-side suction type air-cooled evaporator according to the present invention;

4A is a schematic diagram of a refrigerant in a high temperature evaporation state of a heat pump apparatus employing a double suction type air-cooled evaporator according to the present invention;

Figure 4b is a refrigerant system diagram of a low-temperature evaporation state of the heat pump apparatus employing the one-side suction type air-cooled evaporator according to the present invention.

            <Description of Symbols for Main Parts of Drawings>

10a, 10b: evaporator 20a, 20b: blower

30a: high-temperature electron valve 30b: high-temperature electron valve

31a: high temperature expansion valve 31b: low temperature expansion valve

31c: reverse displacement

40a, 40b: refrigerant inlet pipe 40c: connection pipe

40d, 40e: Distribution pipe 50: Refrigerant outflow pipe

51: liquid separator 52: reverse displacement

 The present invention is used for cold, hot water and cold, heating in large energy consuming places such as sauna, bath, hotel, motel, condo, golf course, golf driving range, sports center, swimming pool, etc. The present invention relates to a heat pump apparatus capable of supplying hot water at a temperature of 60 ° C. to 60 ° C. and cold water at a temperature of 7 ° C. to 12 ° C., and more specifically, using an infinite air heat source in the atmosphere. The present invention relates to an evaporative temperature variable integrated evaporator for heat pump devices that absorbs high-temperature air heat sources and changes the evaporation temperature, heat transfer area, and airflow of the refrigerant to maximize the stable operation, good performance, and energy efficiency of the heat pump device.

In general, the heat pump device uses a variety of methods such as air heat source, waste heat, geothermal heat, solar heat, solar light, etc., but the common technology of heat pump device is air-cooling type that absorbs air heat source because it is relatively simple equipment and simple equipment configuration. Cold and heater heat pump device is the dominant.

And the air-cooled evaporator is an important component of the heat pump device is the most important device for determining the performance and efficiency in the heat pump device.

In Korea, the average image is below 25 ℃ ~ 35 ℃ in summer (summer) and it is formed with very hot weather. In the mid-term (spring, autumn), it is formed in cool weather with average image below 10 ℃ ～ 20 ℃. The environmental changes of the four seasons are so great that they are formed below 15 ℃ ~ 10 ℃. Therefore, it is almost impossible to design a heat exchanger for four seasons in constructing the air volume of the air-cooled evaporator device and the heat transfer area of the evaporator.

Therefore, in the conventional air-cooled cold and heater heat pump device, the coolant evaporation temperature, which determines the performance and efficiency of the heat pump device, is formed at a low temperature below zero as a result of the atmospheric temperature dropping to below zero, resulting in a significant COP. It is difficult to operate the equipment efficiently due to the freezing of the evaporator and the compressor suction of the low temperature part, and the lack of safety due to the liquid hammer phenomenon.In recent years, the compressor type of refrigerant is controlled by the inverter type compressor to solve the problems of safety and freezing. However, the COP is still falling significantly.

In addition, some air-cooled evaporators are used in accordance with the design for sub-zero temperatures for the purpose of using the heat pump system in the winter as much as possible, but instead, in the summer and mid-term periods, because the outside air temperature is too high, The capacity of the air-cooled evaporator, which is designed for use, is too large.

Therefore, in the heat pump device, the refrigerant is sucked into the compressor in the summer and the middle of the evaporator in the superheated state, thereby causing the foaming of the refrigeration oil, the lubrication function is greatly reduced and the oil recovery is seriously concerned, and also the cold refrigerant gas of low pressure A very important function of cooling the compressor is already overheated in the evaporator, which causes a serious problem of the compressor being overheated and damaged.

In addition, it is designed for the low temperature below zero, the external size of the air-cooled evaporator is considerably enlarged, so there is a problem of enormous manufacturing cost, securing the space for installation, and difficult to carry on site. As a result, electric energy consumption is increased, and there are various problems in the field installation construction.

The present invention has been made in view of the problems of the prior art as described above, it is possible to absorb a low-temperature air heat source or a high-temperature air heat source in accordance with environmental changes during the summer and summer, stable operation of the heat pump device and good performance and energy An object of the present invention is to provide an evaporation temperature variable integrated air cooled evaporator for a heat pump device that maximizes efficiency.

Evaporation temperature variable integral air-cooled evaporator for heat pump apparatus of the present invention for achieving the above object is connected to the two evaporator having a predetermined capacity, the evaporator is connected in parallel as absorbing the ambient air heat source to evaporate the refrigerant A blower that induces the flow of air, a high-temperature electromagnetic valve and a high-temperature expansion valve installed in order on a refrigerant inlet pipe for introducing refrigerant into the one evaporator, respectively, and a refrigerant inlet pipe for introducing refrigerant into the other evaporator. A low-temperature electromagnetic valve and a low-temperature expansion valve, respectively, installed in order to the refrigerant pipe, which connects between the refrigerant inlet pipe downstream of the high-temperature expansion valve and the refrigerant inlet pipe downstream of the low-temperature expansion valve, and the refrigerant installed on the connection pipe. It includes a reverse flow that flows only from the low temperature refrigerant inlet pipe to the high temperature refrigerant inlet pipe. It is characterized by.

In addition, the integrated air-cooled evaporator of the present invention is characterized in that the two evaporators are arranged up and down, each of which is a one-sided suction type evaporator.

In addition, the integrated air-cooled evaporator of the present invention, the two evaporators are arranged up and down, and the upper and lower evaporators are two suction type evaporators each consisting of two evaporators left and right, and the left and right evaporators are connected to each other by a distribution pipe. It is done.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Figure 1a is a block diagram of a high-temperature evaporation state of the one-side suction type evaporator as an embodiment of the evaporation temperature variable integral air-cooled evaporator for a heat pump apparatus according to the present invention, Figure 1b is a evaporation temperature variable for a heat pump apparatus according to the present invention. 2 is a schematic diagram of a low temperature evaporation state of a single-sided suction type evaporator, and FIG. 2A illustrates a double side suction type evaporator of another embodiment of the evaporation temperature variable type air cooled type evaporator for a heat pump device according to the present invention. Figure 2b is a schematic diagram of a high temperature evaporation state, Figure 2b is a configuration diagram of a low temperature evaporation state of the two-side suction type evaporator as another embodiment of the evaporation temperature variable integral air cooled evaporator for a heat pump device according to the present invention, Figure 3a Refrigerant system diagram of a high-temperature evaporation state of a heat pump apparatus employing a one-side suction type air-cooled evaporator according to the present invention, and FIG. 4 is a schematic diagram of a refrigerant in a high temperature evaporation state of a heat pump apparatus employing a double side suction type air-cooled evaporator according to the present invention, and FIG. 4b is a single side suction according to the present invention. Refrigerant system diagram of a low-temperature evaporation state of a heat pump apparatus employing a type air-cooled evaporator.

The integrated air-cooled evaporator of one embodiment of the present invention, as shown in Figures 1a, 1b and 2a, 2b is connected in parallel to evaporate the refrigerant by absorbing the ambient air heat source and two evaporators having a predetermined capacity ( 10a) 10b, blowers 20a and 20b for inducing the flow of air to the evaporators 10a and 10b, and on the refrigerant inlet pipe 40a for introducing refrigerant into the evaporator 10a, respectively. The low-temperature electromagnetic valve 30b and the low-temperature electronic valve 30a and the low-temperature electronic valve 30a, respectively, which are installed in this order on the refrigerant inlet pipe 40b for introducing refrigerant into the evaporator 10b. An expansion pipe 31b, a connection pipe 40c for connecting between the refrigerant inlet pipe 40a downstream of the high temperature expansion valve 31a and the refrigerant inlet pipe 40b downstream of the low temperature expansion valve 31b, and the connection pipe ( The refrigerant is installed on 40c) and the refrigerant flows from the refrigerant inlet pipe 40a to the refrigerant inlet pipe 40b. Only comprises a station disaster (31c) to flow to.

The air-cooled evaporator shown in Figs. 1A and 1B is an evaporator in which one evaporator 10a or 10b disposed up and down and air is sucked from one side, and the evaporator shown in Figs. 2A and 2B is an upper and lower evaporator. Two (10a) and two (10b) are evaporators of the type in which air is sucked from both sides.

First, the air-cooled evaporator shown in FIGS. 1A and 1B will be described with reference to FIGS. 3A and 3B. The integrated air-cooled evaporator of this embodiment is a one-side suction type in which air is sucked from one side, and is suitable for the case where the capacity of the heat pump device is small.

In the air-cooled evaporator of this embodiment, the two evaporators 10a and 10b are arranged with one evaporator up and down. The upper and lower evaporators 10a and 10b each have a distributor through which refrigerant flows in parallel. On the refrigerant outflow pipe 50 through which the refrigerant passing through the evaporators 10a and 10b flows out, a liquid separator 51 for separating the liquid contained in the refrigerant and a reverse displacement 52 for preventing backflow of the refrigerant are provided. .

The integrated air-cooled evaporator of this embodiment has two evaporators 10a and 10b divided into upper and lower parts, but the machine is one-piece. When the air heat source is high temperature in the summer and mid-season, it is operated by the high temperature evaporator device so that only the evaporator 10a located at the upper part is operated to effectively cope with the hot air heat source at room temperature. Both the upper and lower evaporators 10a, 10b are operated to effectively respond to cold air heat sources of low temperature.

The integrated air cooled evaporator of this embodiment works as follows.

When the hot gas discharged from the compressor (not shown) of the heat pump device releases heat from the condenser (not shown), it is condensed into the liquid refrigerant gas and supplied to the integrated air-cooled evaporator of the present invention supplying only the liquid refrigerant gas to the evaporator.

As shown in FIG. 3A, during the summer and the middle stage of operating only the upper evaporator 10a, the high-temperature electron valve 30a is opened and the low-temperature electron valve 30b is blocked so that the liquid refrigerant is supplied to the high-temperature expansion valve 31a. It expands into refrigerant gas of low temperature and low pressure. The refrigerant is supplied to the upper evaporator (10a) through a distributor to evenly supply the refrigerant gas by changing to a cool refrigerant gas while maintaining the temperature range of +15 ℃ to -10 ℃. At this time, the refrigerant is blocked so as not to be supplied to the low-temperature evaporator 10b by the reverse direction 31c.

The refrigerant is heat exchanged with the air by the blower 20a for supplying hot air from the evaporator 10a, absorbing the heat source of the air, and the cool refrigerant gas is evaporated to cool the refrigerant discharge pipe through the header of the evaporator (50). To be discharged. The refrigerant separates the liquid refrigerant from the liquid separator 51, and only the gas refrigerant is supplied to the compressor (not shown) for circulation. The state of the summer and the middle stage functions as a high temperature evaporator.

Next, the operation state of the low temperature evaporator operating during the winter season except the summer season and the middle season will be described with reference to FIG. 3B.

When the hot gas discharged from the compressor (not shown) of the heat pump device releases heat from the condenser (not shown), it is condensed into liquid refrigerant gas and supplied to the integrated air-cooled evaporator of the present invention through a receiver which supplies only the liquid refrigerant gas to the evaporator. do.

In the winter season, the high-temperature electron valve 30a operating during the summer and mid-sea periods is closed and the low-temperature electron valve 30b is opened, and the refrigerant is supplied to the low-temperature expansion valve 31b to expand into the low-temperature low-pressure refrigerant gas at low-temperature expansion valve 31b. do. The refrigerant is converted into a cool refrigerant gas while the evaporation temperature is maintained at a low temperature range of + 10 ° C to -25 ° C, and part of the refrigerant passes through the reverse valve 31c to enter the upper evaporator 10a and a part of the lower evaporator 10b. Flows into).

The upper and lower evaporators 10a and 10b each have a distributor so that the refrigerant gas is evenly supplied. The upper and lower evaporators 10a and 10b are also supplied with cool air by the upper and lower blowers 20a and 20b, and heat exchange is performed between the coolant and the cold air. After evaporation is performed by absorbing a heat source, the evaporator is discharged through the hedges of upper and lower evaporators 10a and 10b. The refrigerant is then supplied to the liquid separator 51 on the refrigerant discharge pipe 50 to separate the liquid refrigerant so that only the gas refrigerant is supplied to the compressor (not shown) for circulation.

Thus, during the winter season, the evaporation temperature of the refrigerant is changed to a low temperature below zero by the low-temperature expansion valve 31b, and the heat transfer area is changed by the upper and lower evaporators 10a and 10b to increase the heat transfer area. The blower 20a, 20b makes a variable increase in the blowing amount. This winter condition is a low temperature evaporator.

Next, the bilateral suction air-cooled evaporator shown in FIGS. 2A and 2B will be described with reference to FIGS. 4A and 4B. Both side suction type is suitable for machine configuration when the capacity of heat pump device is large.

The integrated air cooled evaporator of this embodiment operates as shown in FIG. 4A in the summer and intermediate seasons. The heat pump is discharged from the compressor (not shown) of the first heat pump device by passing the heat from the condenser (not shown) and condensed into liquid refrigerant gas and passing through a receiver (not shown) that supplies only the liquid refrigerant gas to the evaporator. One component of the device is fed to the integrated air cooled evaporator of this embodiment.

The high-temperature electron valve 30a operating during the summer and mid-sea periods is opened, and the low-temperature electron valve 30b is blocked, so that the liquid refrigerant is supplied to the high-temperature expansion valve 31a to expand with a low-temperature low-pressure refrigerant gas. The refrigerant is converted into a cold refrigerant gas while maintaining a relatively high temperature range of + 15 ° C to -10 ° C and is supplied to the upper left and right high temperature evaporators 10a. At this time, supply to the low temperature evaporator 10b on the lower left and right sides is prevented by the reverse side 31c. And when the refrigerant gas flows into the left and right evaporator 10a, it is evenly supplied by each distributor.

Since the hot air is supplied to the evaporator 10a by the blower 20a, the cool refrigerant gas absorbs the heat source of the air by heat exchange with the air and evaporates. The evaporated refrigerant gas is integrated through the header of the left and right evaporators 10a, discharged to the refrigerant discharge pipe 5, and supplied to the liquid separator 51, where the liquid refrigerant is separated and only the gas refrigerant is compressed. Continue the cycle supplied to

The action in this state is to act as a high temperature evaporator.

Next, the operation of the low temperature evaporator operating only during the winter season except the summer season and the middle season will be described with reference to FIG. 4B.

As in FIG. 4A, a hot gas discharged from a compressor (not shown) of an initial heat pump device is condensed into liquid refrigerant gas while dissipating heat from a condenser (not shown), and a liquid receiver supplying only liquid refrigerant gas to an evaporator (not shown). And fed to the integrated air cooled evaporator of this embodiment, which is a component of the heat pump apparatus.

In the winter, the high-temperature electron valve 30a is closed and the low-temperature electron valve 30b is opened to supply the liquid refrigerant gas to the low-temperature expansion valve 31b and expand to the low-temperature low-pressure refrigerant gas. The refrigerant gas is converted into cold refrigerant gas while the evaporation temperature is maintained at a relatively low temperature range of + 10 ° C to -25 ° C, and part of the refrigerant gas flows through the reverse direction 31c to the evaporator 10a on the upper left and right, and part directly on the lower side Flows into the evaporator 10b.

The upper and lower evaporators 10a and 10b are each composed of two evaporators. The refrigerant gas is distributed by the distribution pipes 40d and 40e and supplied to the left and right evaporators, respectively. The refrigerant gas is uniformly supplied to each of the evaporators 10a and 10b by a distributor.

Each evaporator 10a, 10b is supplied with cold air below zero by upper and lower blowers 20a, 20b. The cold refrigerant gas evaporates by absorbing a heat source of cold air while exchanging heat with subzero air. do. The refrigerant is integrated through the right and left, upper and lower hedges of the evaporators 10a and 10b to be discharged into the refrigerant discharge pipe 50, and the liquid refrigerant is separated from the liquid separator 51 so that only the gas refrigerant is compressed. Continue the cycle supplied to

Thus, during the winter season, the evaporation temperature of the refrigerant is changed to a low temperature below zero by the low-temperature expansion valve 31b, and the heat transfer area is changed by the upper and lower evaporators 10a and 10b to increase the heat transfer area. The blower 20a, 20b makes a variable increase in the blowing amount. This winter condition is a low temperature evaporator.

The integrated air-cooled evaporator of the present invention is suitable for the Korean atmospheric environment, which is composed at room temperature in the summer and mid-season, and is formed at low temperature below freezing in the winter season.

According to the present invention, during the summer and middle seasons, the expansion range of the temperature range of + 15 ° C. to −10 ° C. in which the evaporation temperature is used for high temperature is operated, and the evaporator 10a operates in accordance with the heat transfer area of the evaporator. The expansion range of -25 ° C. to + 10 ° C., where the evaporation temperature is for low temperature, is operated, and the two evaporators 10a and 10b are operated to fit the heat transfer area of the evaporator for low temperature. The amount of air sent to the evaporator also changes with the season. In the summer and middle season, only the blower 20a located at the upper part is operated to adjust the air volume, and in the winter season, both the upper and lower blowers 20a and 20b are operated to increase the air flow amount. By doing so, it works in response to any seasonal changes in the environment.

As described above, the evaporation temperature variable integrated air-cooled evaporator for heat pump apparatus according to the present invention is configured to adjust the evaporation temperature, the heat transfer area, and the blowing amount of the refrigerant so as to absorb a low-temperature air heat source or a high-temperature air heat source according to environmental changes in winter and summer. Since it is variable, it is possible to operate the heat pump device stably during the four seasons, and to maintain good performance and good energy efficiency at all times, and because the external size is not large, the manufacturing cost is low and the space for installation is secured and the site It is easy to carry in and install, and the air volume is not big enough to save electric energy without causing noise.

Claims (3)

Two evaporators 10a and 10b connected in parallel and absorbing an air source around the air and having a predetermined capacity, Blowers 20a and 20b for inducing the flow of air to the evaporators 10a and 10b, The high-temperature electron valve 30a and the high-temperature expansion valve 31a, which are respectively installed in order on the refrigerant inlet pipe 40a for introducing the refrigerant to the evaporator 10a, The low-temperature electron valve 30b and the low-temperature expansion valve 31b, which are respectively installed in order on the refrigerant inlet pipe 40b for introducing the refrigerant to the evaporator 10b, A connection pipe 40c connecting between the refrigerant inlet pipe 40a downstream of the high temperature expansion valve 31a and the refrigerant inlet pipe 40b downstream of the low temperature expansion valve 31b, and Evaporation temperature variable type for the heat pump device, characterized in that it is provided on the connecting pipe (40c) comprises a reverse flow 31c for the refrigerant flows from the refrigerant inlet pipe (40a) only to the refrigerant inlet pipe (40b). Integrated air cooled evaporator. The method of claim 1, wherein the two evaporators (10a, 10b) are arranged up and down, each of the single-side suction type evaporator consisting of one evaporator, the evaporation temperature variable integral air-cooled evaporator for a heat pump device. According to claim 1, wherein the two evaporators (10a, 10b) are arranged up and down, and the upper and lower evaporators (10a, 10b) are two suction type evaporator each consisting of two evaporators left and right, the left and right evaporators respectively An evaporating temperature variable integrated air cooling evaporator for a heat pump device, characterized in that connected to each other by a distribution pipe (40d) (40e).

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