KR20180053853A - Heat Pump System - Google Patents

Abstract

The present invention relates to a heat pump system, and specifically comprises: a compressor provided in an outdoor unit and compressing a refrigerant; at least one indoor unit provided with an indoor heat exchanger selectively guided with the refrigerant discharged from the compressor, and arranged in a location lower than that of the outdoor unit; an outdoor heat exchanger selectively guided with the refrigerant discharged from the compressor; and an accumulator provided at the front end of the compressor within the outdoor unit and formed to supply only a gas state refrigerant to the compressor, wherein the refrigerant condensed in the indoor heat exchanger is condensed through a subsidiary condensation flow path before passing a first main expansion valve of the front end of the outdoor heat exchanger in a heating mode.

Description

[0001] Heat Pump System [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a heat pump system, and more particularly, to a heat pump system capable of preventing a decrease in the flow rate of circulating refrigerant and a decrease in heating performance due to a pressure loss of refrigerant flowing from an indoor unit to an outdoor unit in a heating mode.

Generally, a heat pump system represents a system capable of cooling or heating the air conditioning space based on the circulation of the refrigerant compressed by the compressor.

1 is a view showing an outdoor unit of a conventional heat pump system.

Referring to FIG. 1, in a conventional heat pump system, in a heating mode, refrigerant discharged from the compressor 2 is guided toward the indoor unit 3. The indoor unit 3 is provided with an indoor heat exchanger (not shown), and the refrigerant in the indoor heat exchanger can be condensed and the air conditioning space can be heated.

The refrigerant condensed in the indoor unit (3) is led to the outdoor unit (1). The refrigerant flowing into the outdoor unit (1) is expanded in the expansion valve (4) and then flows into the outdoor heat exchanger (5) and evaporated.

After the refrigerant having passed through the outdoor heat exchanger is separated into the gaseous refrigerant and the liquid refrigerant in the accumulator 6, only the gaseous refrigerant is guided to the compressor 2.

On the other hand, when a heat pump system is installed in a building, the outdoor unit 1 is installed on the roof and the indoor unit 3 is installed in the air conditioning space in the building.

Particularly, when a heat pump system is installed in a high-rise building having a predetermined height or higher, the distance between the outdoor unit 1 and the indoor unit 3 is relatively increased and the height of the outdoor unit 1 and the indoor unit 3 A difference is generated.

A pressure loss (also referred to as "head loss") occurs in the course of the refrigerant condensed in the indoor unit 3 flowing toward the outdoor unit 1 when a height difference of a predetermined size or more is generated between the outdoor unit 1 and the indoor unit 3 .

When the pressure of the refrigerant guided from the indoor unit 3 to the outdoor unit 1 is lowered, the proportion of the gaseous refrigerant gradually increases.

At this time, when the abnormal refrigerant in a state in which the ratio of the gaseous refrigerant is increased passes through the expansion valve 4 provided at the front end of the outdoor heat exchanger 5, the flow rate of the refrigerant passing through the expansion valve 4 becomes Can be relatively reduced as compared with the case of passing through the expansion valve (4).

If the flow rate of the refrigerant passing through the expansion valve 4 is reduced, the high and low pressures of the system may be lowered, and as a result, the heating performance may deteriorate.

That is, according to the conventional heat pump system, since the flow rate of the refrigerant circulating in the heat pump system in the heating mode is decreased due to the difference in installation height between the outdoor unit 1 and the indoor unit 3, .

SUMMARY OF THE INVENTION It is an object of the present invention to provide a heat pump system capable of compensating for a pressure loss of a refrigerant according to an installed position of an outdoor unit and an indoor unit.

It is another object of the present invention to provide a heat pump system in which, in a heating mode, a refrigerant can increase a flow rate of a refrigerant passing through an expansion valve at a front end of an outdoor heat exchanger.

Another object of the present invention is to provide a heat pump system capable of preventing deterioration of heating performance even when the outdoor unit is installed at a predetermined height or higher than the indoor unit.

According to a first aspect of the present invention, there is provided a refrigerator comprising: a compressor provided in an outdoor unit for compressing refrigerant; At least one indoor unit having an indoor heat exchanger in which a refrigerant discharged from the compressor is selectively guided, and disposed at a lower position than the outdoor unit; An outdoor heat exchanger for selectively guiding the refrigerant discharged from the compressor; And an accumulator provided at the front end of the compressor in the outdoor unit and configured to supply only the gaseous refrigerant to the compressor, wherein in the heating mode, the refrigerant condensed in the indoor heat exchanger flows through the first main expansion And is condensed through the auxiliary condensing flow passage before passing through the valve.

And a first branch flow path and a second branch flow path for branching the refrigerant flowing into the outdoor unit after being condensed in the indoor unit.

At this time, a part of the refrigerant flowing into the outdoor unit is guided to the auxiliary condensing flow passage through the first branch flow passage, and the remainder of the refrigerant flowing into the outdoor unit flows into the receiver provided at the lower end of the accumulator through the second branch flow passage Can be informed.

Further, the heat pump system according to the first embodiment may further include an auxiliary evaporation flow path for heat exchange with the auxiliary condensation flow path, and the liquid phase refrigerant in the receiver may be guided to the auxiliary evaporation flow path.

Further, an auxiliary expansion valve may be provided between the receiver and the auxiliary evaporation flow path.

The first branch passage may include a first check valve formed in a direction toward the auxiliary condensing passage, and a second check valve may be provided between the receiver and the auxiliary expansion valve in a direction toward the auxiliary evaporation passage .

The refrigerant in the auxiliary condensing flow passage and the refrigerant in the auxiliary evaporation flow passage can exchange heat with each other in the auxiliary heat exchange section.

Wherein the first branch flow passage is provided with a first flow control valve and the second branch flow passage is provided with a second flow control valve, and the first flow control valve and the second flow control valve are controlled by a predetermined high pressure and predetermined sub- The opening degree can be adjusted on the basis of the degree.

In the cooling mode of the heat pump system according to the first embodiment, the refrigerant condensed in the outdoor heat exchanger can be supercooled while passing through the auxiliary condensing duct of the auxiliary heat exchanger. A part of the refrigerant passing through the auxiliary condensing passage may be branched and may be guided to the accumulator after being evaporated while sequentially passing through the auxiliary expansion valve and the auxiliary evaporation passage.

Meanwhile, the heat pump system according to the second embodiment of the present invention is provided in an outdoor unit, and includes a compressor for compressing a refrigerant; At least one indoor unit having an indoor heat exchanger in which a refrigerant discharged from the compressor is selectively guided, and disposed at a lower position than the outdoor unit; An outdoor heat exchanger for selectively guiding the refrigerant discharged from the compressor; And an accumulator provided at the front end of the compressor in the outdoor unit and configured to supply only gaseous refrigerant to the compressor.

In this case, the heat pump system according to the second embodiment includes a receiver installed at the lower end of the accumulator and guided by the refrigerant condensed in the indoor heat exchanger; A first branched flow path for guiding a part of the liquid refrigerant discharged from the receiver toward the outdoor heat exchanger; And a second branched flow path for guiding the remainder of the liquid refrigerant discharged from the receiver to the auxiliary evaporation flow path in the receiver.

Further, an auxiliary expansion valve may be provided at a front end of the auxiliary evaporative flow passage.

In the first and second embodiments, the accumulator and the receiver are integrally formed as a single case, a partition plate is provided between the accumulator and the receiver, and the partition plate may be formed of a thermally conductive member .

In addition, a discharge port through which the discharge passage is connected is formed on a lower surface of the receiver, and an inlet port through which the refrigerant condensed in the indoor heat exchanger flows is formed on a side surface of the receiver. At this time, the inlet may be disposed closer to the partition plate than the lower surface of the receiver.

The heat pump system according to the first and second embodiments includes an engine for driving the compressor; A cooling water passage through which cooling water for cooling the engine flows; And a plate type heat exchanger for exchanging a part of the refrigerant guided toward the outdoor heat exchanger through the first branch flow path with the cooling water.

The heat pump system may further include a third branch flow channel branched from the first branch flow channel toward the outdoor heat exchanger and a fourth branch flow channel branched toward the plate heat exchanger. At this time, the first main expansion valve may be provided in the third branch flow passage, and the second main expansion valve may be provided in the fourth branch flow passage.

In the cooling mode of the heat pump system according to the second embodiment, the refrigerant condensed in the outdoor heat exchanger can be guided to the inlet of the receiver. A part of the refrigerant discharged from the discharge port of the receiver and directed toward the indoor unit is guided to the auxiliary evaporation flow path through the second branch flow path to perform heat exchange with the refrigerant in the receiver.

According to the present invention, it is possible to provide a heat pump system capable of compensating a pressure loss of a refrigerant according to installation positions of an outdoor unit and an indoor unit.

Further, according to the present invention, it is possible to provide a heat pump system in which the refrigerant can increase the flow rate of the refrigerant passing through the expansion valve in the front end of the outdoor heat exchanger in the heating mode.

Further, according to the present invention, it is possible to provide a heat pump system capable of preventing deterioration of heating performance even when the outdoor unit is installed at a predetermined height or higher than the indoor unit.

1 is a view showing an outdoor unit of a conventional heat pump system.
2 is a view showing a heat pump system according to the present invention.
3 is a view showing a heating mode of the heat pump system according to the first embodiment of the present invention.
4 is a view showing a cooling mode of the heat pump system according to the first embodiment of the present invention.
5 is a view showing a heating mode of the heat pump system according to the second embodiment of the present invention.
6 is a view showing a cooling mode of the heat pump system according to the second embodiment of the present invention.

Hereinafter, an air conditioner according to the present invention will be described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the principles of the invention.

In addition, the same or corresponding components are denoted by the same reference numerals regardless of the reference numerals, and redundant description thereof will be omitted. For convenience of explanation, the size and shape of each constituent member shown may be exaggerated or reduced have.

2 is a view showing a heat pump system according to the present invention.

Referring to FIG. 2, the heat pump system 10 may include an outdoor unit 20 installed outdoors and at least one indoor unit 30 installed in an air conditioning space (indoor). Although one outdoor unit 20 is shown in the illustrated embodiment, a plurality of outdoor units 20 and a plurality of indoor units 30 may be provided.

The outdoor unit (20) may be disposed on the roof of the building, and the indoor unit (30) may be disposed in the air conditioning space provided below the roof.

At this time, a distance difference and a height difference may be generated between the outdoor unit 20 and the indoor unit 30 as the indoor unit 30 is installed in the lower layer of the building. Particularly, due to the height difference between the outdoor unit 20 and the indoor unit 30, a pressure loss of the refrigerant flowing from the indoor unit 30 toward the outdoor unit 20 in the heating mode can be generated.

Specifically, when the difference in height between the outdoor unit 20 and the indoor unit 30 is greater than a predetermined height, the refrigerant condensed in the indoor unit 30 in the heating mode flows toward the outdoor unit 20 The ratio of the gaseous refrigerant can be increased due to the pressure drop of the refrigerant.

On the other hand, as the ratio of the gaseous refrigerant increases, the flow rate of the refrigerant passing through the expansion valve, which will be described later, may be reduced, which may lead to a decrease in the heating performance.

Therefore, it is preferable to minimize the ratio of the gaseous refrigerant before the refrigerant enters the expansion valve provided in the outdoor unit (in the front end of the outdoor heat exchanger) in the heating mode.

Hereinafter, with reference to other drawings, a description will be given of a configuration in which the ratio of the gaseous refrigerant can be minimized before the refrigerant flows into the expansion valve.

3 is a view showing a heating mode of the heat pump system according to the first embodiment of the present invention.

Referring to FIG. 3, the heat pump system 10 according to the first embodiment of the present invention may include an outdoor unit 20 and at least one indoor unit 30. FIG. In the figure, one indoor unit 30 is shown, but as shown in FIG. 2, a plurality of indoor units 30 may be provided.

The indoor unit (30) can be disposed at a lower position than the outdoor unit (20). That is, the outdoor unit 20 is disposed on the roof of the building and the indoor unit 30 is disposed inside the building below the roof, so that the outdoor unit 20 can be disposed at a higher position than the indoor unit 30.

The indoor unit 30 may include an indoor heat exchanger 600 and the indoor heat exchanger 600 may include an indoor fan 610 at one side thereof.

The indoor heat exchanger 600 may be formed to exchange heat between the air in the air conditioning space (indoor space) and the refrigerant. The indoor heat exchanger 600 may operate as a condenser in a heating mode and as an evaporator in a cooling mode.

The outdoor unit 20 may include a compressor 100, a flow path switching valve 200, an outdoor heat exchanger 300, an accumulator 400, and an auxiliary heat exchanger 500.

The compressor 100 may be driven by the engine E and may be configured to compress the refrigerant.

The flow path switching valve 200 may be formed as a four way valve. The flow path switching valve 200 may be configured to selectively guide the refrigerant discharged from the compressor 100 to the outdoor heat exchanger 300 or the indoor heat exchanger 600.

In the heating mode, the refrigerant discharged from the compressor 100 is guided to the indoor heat exchanger 600 through the flow path switching valve 200. In the cooling mode, the refrigerant discharged from the compressor 100 is guided to the outdoor heat exchanger 300 through the flow path switching valve 200.

The outdoor heat exchanger 300 may be formed to exchange heat between the outdoor air and the refrigerant. The outdoor heat exchanger 300 may be operated as an evaporator in a heating mode and as a condenser in a cooling mode.

A first main expansion valve 710 may be provided on one side of the outdoor heat exchanger 300. The first main expansion valve 710 may be disposed at a front end (inlet side) of the indoor heat exchanger 300 in a heating mode. The first main expansion valve 710 may expand the refrigerant flowing into the outdoor heat exchanger 300 in the heating mode.

The accumulator 400 may be provided at the front end (inlet side) of the compressor 100. The accumulator 400 may be configured to separate the abnormal refrigerant into the gaseous refrigerant and the liquid refrigerant. That is, the accumulator 400 may be configured to supply only the gaseous refrigerant to the compressor 100.

On the other hand, in the heating mode, when the abnormal refrigerant flows into the first main expansion valve 710, the flow rate of the refrigerant passing through the first main expansion valve 710 decreases, and the heating performance may decrease. That is, it is advantageous that the ratio of the gaseous refrigerant to the refrigerant passing through the first main expansion valve 710 is as small as possible. In other words, it is preferable that only the liquid refrigerant passes through the first main expansion valve 710.

The heat pump system 10 according to the first embodiment of the present invention may further include an auxiliary condensing flow path 520. The refrigerant condensed in the indoor heat exchanger 600 may be condensed through the auxiliary condensing flow passage 520 before passing through the first main expansion valve 710 at the front end of the outdoor heat exchanger 300.

That is, the refrigerant condensed in the indoor heat exchanger 600 may be condensed again through the auxiliary condensing flow passage 520 before passing through the first main expansion valve 710. Therefore, in the heating mode, the ratio of the gaseous refrigerant to the pressure loss of the refrigerant flowing from the indoor unit 30 to the outdoor unit 20 can be reduced or eliminated through the auxiliary condensing duct 520.

Specifically, the heat pump system 10 according to the first embodiment of the present invention may include an auxiliary heat exchanging part 500 for condensing the refrigerant guided to the first main expansion valve 710

In the heating mode, the auxiliary heat exchanging unit 500 is provided in the outdoor unit 20 at the front end of the first main expansion valve 710 to condense the refrigerant guided toward the first main expansion valve 710 .

The heat pump system 10 may include a first branch flow channel 810 and a second branch flow channel 820 for branching the refrigerant guided from the indoor unit 30 to the outdoor unit 20. The refrigerant condensed in the indoor unit (30) is guided toward the outdoor unit (20) through the main flow path (800).

The refrigerant flowing into the outdoor unit 20 through the main channel 800 after being condensed in the indoor unit 30 flows through the first branched flow channel 810 and the second branched flow channel 820 in the outdoor unit 20, .

Part of the refrigerant flowing into the outdoor unit 20 after being condensed in the indoor unit 30 may be guided to the auxiliary condensing duct 510 through the first branch flow channel 810.

The remaining portion of the refrigerant flowing into the outdoor unit 20 after being condensed in the indoor unit 30 can be guided to the receiver 450 through the second branch line 820. The receiver 450 may be provided at the lower end of the accumulator 400.

The accumulator 400 and the receiver 450 may be integrally formed as a single case. Specifically, in one case, the accumulator 400 may be provided on the upper portion and the receiver 450 may be provided on the lower portion.

A partition plate 430 may be provided between the accumulator 400 and the receiver 450. The partition plate 430 may be formed of a thermally conductive member. Therefore, the refrigerant in the accumulator 400 can exchange heat with the refrigerant in the receiver 450.

That is, the abnormal refrigerant supplied into the receiver 450 can be condensed by heat exchange with the liquid refrigerant in the accumulator 400. The liquid refrigerant accumulated in the accumulator 400 may be evaporated through heat exchange with the ideal refrigerant supplied into the receiver 450.

The heat pump system 10 may further include an auxiliary evaporation flow path 520 for exchanging heat with the auxiliary condensing flow path 510. The liquid refrigerant in the receiver 450 can be guided to the auxiliary evaporation flow path 520.

That is, the refrigerant in the auxiliary condensing flow passage 510 and the refrigerant in the auxiliary evaporation flow passage 520 are heat-exchanged, so that the refrigerant in the auxiliary condensing flow passage 510 is condensed and the refrigerant in the auxiliary evaporation flow passage 520 can be evaporated.

The auxiliary condensing flow path 510 and the auxiliary evaporation flow path 520 may be disposed in the auxiliary heat exchanging part 500. Therefore, the refrigerant in the auxiliary condensing flow passage 510 and the refrigerant in the auxiliary evaporation flow passage 520 can exchange heat with each other in the auxiliary heat exchanging part 500.

An auxiliary expansion valve 730 may be provided between the receiver 450 and the auxiliary evaporation flow path 520. The auxiliary expansion valve 730 may be formed to expand the liquid refrigerant guided from the receiver 450 to the auxiliary evaporation flow path 520.

The first branch passage 810 may include a first check valve 811 formed in a direction toward the auxiliary condensation passage 510. A second check valve 821 may be provided between the receiver 450 and the auxiliary expansion valve 730 in a direction toward the auxiliary evaporation flow passage 520. The refrigerant channel in the heating mode can be distinguished from the refrigerant channel in the cooling mode by the first check valve 811 and the second check valve 821. [

A first flow control valve 812 may be provided in the first branch flow channel 810 and a second flow control valve 822 may be provided in the second branch flow channel 820. The openings of the first flow control valve 812 and the second flow control valve 822 can be adjusted based on the previously set high pressure and predetermined subcooling degree.

The flow rate of the refrigerant guided toward the outdoor heat exchanger 300 after being condensed in the auxiliary condensing flow passage 510 can be determined by adjusting the opening of the first flow control valve 812. The flow rate of the refrigerant guided to the accumulator 400 can be determined by sequentially passing through the receiver 430 and the auxiliary evaporation flow passage 520 by adjusting the opening degree of the second flow rate control valve 822.

The heat pump system 10 according to the present invention may further include a cooling water passage C through which cooling water for cooling the engine E flows.

The cooling water flow path C may be formed to pass through a plate type heat exchanger 900 to be described later and the cooling water in the cooling water flow path C may be cooled in the plate type heat exchanger 900.

For example, a part of the refrigerant guided toward the outdoor heat exchanger 300 through the auxiliary condensing duct 510 may be branched and guided to the plate heat exchanger 900. The refrigerant guided to the plate-type heat exchanger 900 can be evaporated by heat exchange with the cooling water in the cooling water flow path (C).

Specifically, the refrigerant that has passed through the auxiliary discharge channel 510 may be branched into the third branch flow channel 830 and the fourth branch flow channel 840.

The refrigerant branched to the third branch flow path 830 is guided toward the outdoor heat exchanger 300. The refrigerant branched to the fourth branch flow path 840 is guided to the plate type heat exchanger 900. The fourth branched flow path 840 may pass through the plate type heat exchanger 900 and exchange heat with the cooling water flow path C in the plate type heat exchanger 900.

The fourth branch flow passage 840 is provided with a second main expansion valve 720 and the second main expansion valve 720 may be provided at a front end of the plate heat exchanger 900. Therefore, the refrigerant guided to the fourth branched flow path 840 is expanded through the second main expansion valve 720, and then is heat-exchanged with the cooling water in the cooling water flow path C in the plate type heat exchanger 900 .

The refrigerant guided through the third branch flow channel 830 and evaporated in the external heat exchanger 300 and the refrigerant guided through the fourth branch flow channel 840 and evaporated in the plate heat exchanger 900 are joined to each other, (Not shown).

The flow of the refrigerant in the heating mode of the heat pump system according to the first embodiment of the present invention is summarized as follows.

The refrigerant discharged from the compressor (100) is condensed in the indoor heat exchanger (600). The refrigerant passing through the indoor heat exchanger 600 and flowing into the outdoor unit 20 is branched through the first branch flow channel 810 and the second branch flow channel 820.

The refrigerant guided through the first branch flow path 810 is condensed in the auxiliary heat exchanging part 500 and then guided toward the outdoor heat exchanger 300. In the former part of the outdoor heat exchanger 300, 900 < / RTI >

The refrigerant guided through the second branch flow passage 820 is evaporated in the auxiliary heat exchanging part 500 via the receiver 450 and then supplied to the accumulator 400.

As described above, even if pressure loss occurs in the refrigerant flowing from the indoor unit 30 to the outdoor unit 20 due to a difference in installation height between the outdoor unit 20 and the indoor unit 30, the refrigerant is condensed in the auxiliary heat exchanging unit 500 . Therefore, it is possible to prevent the flow rate of the refrigerant passing through at least one of the first main expansion valve 710 and the second main expansion valve 720 from decreasing.

Further, by securing the flow rate of the refrigerant passing through at least one of the first main expansion valve 710 and the second main expansion valve 720, deterioration in the heating performance of the heat pump system can be prevented.

Hereinafter, the refrigerant flow in the cooling mode of the heat pump system according to the first embodiment of the present invention will be described with reference to other drawings.

4 is a view showing a cooling mode of the heat pump system according to the first embodiment of the present invention.

Referring to FIG. 4, in the cooling mode, the refrigerant discharged from the compressor 100 may be guided to the outdoor heat exchanger 300 through the flow path switching valve 200.

The refrigerant condensed in the outdoor heat exchanger (300) can be supercooled while passing through the auxiliary condensing duct (510) of the auxiliary heat exchanger (500).

Part of the refrigerant that has passed through the auxiliary condensing passage 510 may be branched and may be guided to the accumulator 400 via the auxiliary expansion valve 730 and the auxiliary evaporation passage 520 in order. The refrigerant in the auxiliary condensing flow path 510 can be supercooled through the heat exchange between the refrigerant in the auxiliary condensing flow path 510 and the refrigerant in the auxiliary evaporation flow path 520.

That is, in the cooling mode, the supercooling degree of the refrigerant supplied to the indoor unit (30) can be secured through the auxiliary heat exchanging unit (500). When the predetermined subcooling degree of the refrigerant is secured through the auxiliary heat exchanging part 500, the saturation latent heat of the refrigerant is increased, so that the cooling ability can be improved.

The remainder of the refrigerant that has passed through the auxiliary condensing flow path 510 can be guided toward the indoor unit 30. [ At this time, a part of the refrigerant guided toward the indoor unit 30 may be supplied to the receiver 450 via the main flow channel 800 and the second branch flow channel 820 based on the cooling performance.

The liquid refrigerant accumulated in the receiver 450 may be selectively supplied to the accumulator 400 through a connection line 453 connecting the receiver 450 and the accumulator 400. The connection line 453 may include a solenoid valve 455.

The refrigerant evaporated in the indoor heat exchanger 600 in the indoor unit 30 can be supplied to the accumulator 400 via the flow path switching valve 200. The gaseous refrigerant separated by the ac miculator 600 may be supplied to the compressor 100 again.

The cooling water passage C of the engine E is connected to the auxiliary outdoor heat exchanger 350 disposed at one side of the outdoor heat exchanger 300 .

That is, in the cooling mode, the refrigerant in the cooling water flow path C can be cooled by heat exchange with the outdoor air through the auxiliary outdoor heat exchanger 350.

Hereinafter, a heat pump system according to a second embodiment of the present invention will be described with reference to other drawings.

5 is a view showing a heating mode of the heat pump system according to the second embodiment of the present invention. In explaining the second embodiment of the heat pump system, detailed description of the same configuration as the first embodiment described above will be omitted. For convenience of explanation, the same reference numerals are used for the components corresponding to those of the first embodiment in the second embodiment.

5, the heat pump system 10 according to the second embodiment of the present invention includes a compressor 100, a flow path switching valve 200, an outdoor heat exchanger 300, an accumulator (not shown) 400, a receiver 450, and an indoor heat exchanger 600.

Unlike the first embodiment, the heat pump system 10 according to the second embodiment does not have an auxiliary heat exchanger. Unlike the first embodiment, according to the second embodiment, the refrigerant guided from the heating mode to the outdoor heat exchanger can be condensed in the receiver 450. [

As described above, the receiver 450 may be provided integrally with the accumulator 400 at the lower end of the accumulator 400.

The refrigerant condensed in the indoor heat exchanger (600) may be guided to the receiver (450). Specifically, the refrigerant condensed in the indoor heat exchanger 600 can be guided to the receiver 450 through the main flow path 800. The abnormal refrigerant may flow into the receiver 450 and the liquid refrigerant may accumulate on the floor. The gaseous refrigerant in the abnormal refrigerant flowing into the receiver 450 can be condensed by heat exchange with the liquid refrigerant in the accumulator 400 located above the receiver 450.

That is, as described above, the accumulator 400 and the receiver 450 are integrally formed as a single case and can be partitioned by the partition plate 430 which is a thermally conductive member. Therefore, the refrigerant in the accumulator 400 and the refrigerant in the receiver 450 can exchange heat with each other.

The liquid refrigerant in the receiver 450 may be discharged from the receiver 450 through the discharge passage 801.

The heat pump system 10 according to the second embodiment includes a first branch flow passage 810 for guiding a part of the liquid refrigerant discharged from the receiver 450 toward the outdoor heat exchanger 300, And a second branched flow passage 820 for guiding the remainder of the discharged liquid refrigerant to the auxiliary evaporation flow passage 520 in the receiver 450.

That is, the liquid refrigerant in the receiver 450 can be discharged from the receiver 450 through the discharge passage 801. The refrigerant guided through the discharge passage 801 may be branched through the first branch passage 810 and the second branch passage 820.

The first branched flow passage 810 can guide a part of the liquid refrigerant discharged from the receiver 450 toward the outdoor heat exchanger 300. The second branched flow passage 820 can guide the remainder of the liquid refrigerant discharged from the receiver 450 toward the auxiliary evaporation flow passage 520.

The auxiliary expansion valve 730 may be provided at the front end (inlet side) of the auxiliary evaporation flow passage 520. Specifically, the auxiliary branch valve 730 may be provided in the second branch passage 820. Therefore, the refrigerant guided to the auxiliary evaporation flow path 520 may be evaporated in the auxiliary evaporation flow path 520 after being expanded through the auxiliary expansion valve 730.

That is, the refrigerant in the auxiliary evaporation flow passage 520 can be evaporated by heat exchange with the refrigerant in the receiver 450. The refrigerant in the receiver 450 may be condensed by heat exchange with the refrigerant in the auxiliary evaporation flow path 520.

Accordingly, it is possible to prevent the abnormal refrigerant from being guided to the first main expansion valve 710 at the front end (inlet side) of the outdoor heat exchanger 300 through the first branched flow path 810. That is, the gaseous refrigerant can be prevented from flowing into the first main expansion valve 710 by the heat exchange between the refrigerant in the receiver 450 and the refrigerant in the auxiliary evaporation flow passage 520.

Meanwhile, a discharge port 452 connected to the discharge passage 801 may be formed on a lower surface of the receiver 450. Therefore, the liquid refrigerant accumulated in the receiver 450 can be easily discharged through the discharge passage 801. [

An inlet port 451 through which the refrigerant condensed in the indoor heat exchanger 300 flows may be formed on the side of the receiver 450. At this time, the inlet port 451 may be disposed closer to the partition plate 430 than the lower surface of the receiver 450. That is, the inlet 451 may be disposed adjacent to the partition plate 430.

That is, when the abnormal refrigerant flows into the receiver 450, the liquid refrigerant can be accumulated on the floor and the gaseous refrigerant can be positioned relatively upward. Therefore, only the liquid refrigerant in the receiver 450 can be discharged through the discharge passage 801. [ The gaseous refrigerant in the receiver 450 may be heat-exchanged with the liquid refrigerant in the accumulator 400 or the refrigerant in the auxiliary evaporation flow passage 520 to be condensed.

The heat pump system 10 according to the second embodiment includes the engine E for driving the compressor 100 and the cooling water flow path through which the cooling water for cooling the engine E flows C).

The heat pump system 10 further includes a plate type heat exchanger 900 for exchanging a part of the refrigerant guided to the outdoor heat exchanger 300 through the first branch flow path 810 with the cooling water .

That is, the first branch flow channel 810 may be branched into a third branch flow channel 830 toward the outdoor heat exchanger 300 and a fourth branch flow channel 840 toward the plate heat exchanger 900. The third branch flow passage 830 may include the first main expansion valve 710 and the fourth branch flow passage 840 may include a second main expansion valve 720.

The cooling water in the cooling water passage C and the refrigerant in the fourth branch passage 840 can exchange heat with each other in the plate heat exchanger 900.

The flow of the refrigerant in the heating mode of the heat pump system according to the second embodiment of the present invention is summarized as follows.

The refrigerant discharged from the compressor (100) is condensed in the indoor heat exchanger (600). The refrigerant passing through the indoor heat exchanger 600 and flowing into the outdoor unit 20 is guided into the receiver 450 through the main flow channel 800.

The liquid refrigerant in the receiver 450 is branched into a first branched flow path 810 discharged through the discharge flow path 801 toward the outdoor heat exchanger and a second branched flow path 810 directed to the auxiliary evaporation flow path 520 in the receiver .

The refrigerant guided to the second branched flow path 810 is expanded in the auxiliary expansion valve 730 and then guided to the auxiliary evaporation flow path 520 and evaporated. That is, the refrigerant in the auxiliary evaporation flow passage 520 and the refrigerant in the receiver 450 exchange heat, so that the refrigerant in the receiver 450 can be condensed.

That is, after the refrigerant is condensed in the receiver 450, the refrigerant guided to the first branch flow path 810 is guided toward the silencer heat exchanger 300 and evaporated in the outdoor heat exchanger 300, Some of the refrigerant may be branched toward the plate heat exchanger 900 and evaporated in the plate heat exchanger 900.

The refrigerant evaporated in the outdoor heat exchanger 300, the refrigerant evaporated in the plate heat exchanger 900, and the refrigerant evaporated in the auxiliary evaporation passage 520 may be combined and supplied to the accumulator 400.

As described above, even if pressure loss occurs in the refrigerant flowing from the indoor unit 30 to the outdoor unit 20 due to a difference in installation height between the outdoor unit 20 and the indoor unit 30, the refrigerant is condensed in the receiver 400 And then to the outdoor heat exchanger (300). Therefore, it is possible to prevent the flow rate of the refrigerant passing through at least one of the first main expansion valve 710 and the second main expansion valve 720 from decreasing.

Further, by securing the flow rate of the refrigerant passing through at least one of the first main expansion valve 710 and the second main expansion valve 720, deterioration in the heating performance of the heat pump system can be prevented.

Hereinafter, the refrigerant flow in the cooling mode of the heat pump system according to the second embodiment of the present invention will be described with reference to other drawings.

6 is a view showing a cooling mode of the heat pump system according to the second embodiment of the present invention.

Referring to FIG. 6, in the cooling mode, the refrigerant discharged from the compressor 100 may be guided to the outdoor heat exchanger 300 through the flow path switching valve 200.

The refrigerant condensed in the outdoor heat exchanger 300 is guided into the receiver 450 through the connection passage 850 connecting the fourth branch passage 840 and the main passage 800 described above.

The refrigerant guided to the receiver 450 may be supercooled by heat exchange with the refrigerant in the auxiliary evaporation flow passage 520 disposed in the receiver 450. That is, in the cooling mode, the supercooling degree of the refrigerant supplied to the indoor unit (30) can be secured through the auxiliary heat exchanging unit (500). When the predetermined subcooling degree of the refrigerant is secured through the auxiliary heat exchanging part 500, the saturation latent heat of the refrigerant is increased, so that the cooling ability can be improved.

The refrigerant supercooled in the receiver 450 can be discharged through the discharge passage 801 and guided toward the indoor unit 30. [ At this time, some of the refrigerant is branched into the second branch flow path 820, and the refrigerant can be evaporated sequentially through the auxiliary expansion valve 730 and the auxiliary evaporation flow path 520.

The refrigerant vaporized in the auxiliary evaporation flow path 520 may be combined with the refrigerant vaporized in the indoor heat exchanger 600 and supplied to the accumulator 400. The gaseous refrigerant separated by the ac miculator 600 may be supplied to the compressor 100 again.

The cooling water passage C of the engine E is connected to the auxiliary outdoor heat exchanger 350 disposed at one side of the outdoor heat exchanger 300 .

That is, in the cooling mode, the refrigerant in the cooling water flow path C can be cooled by heat exchange with the outdoor air through the auxiliary outdoor heat exchanger 350.

The foregoing description of the preferred embodiments of the present invention has been presented for purposes of illustration and various modifications, additions and substitutions are possible, without departing from the scope and spirit of the invention, And additions should be considered as falling within the scope of the following claims.

100 compressor 200 Euro switching valve
300 outdoor heat exchanger 400 accumulator
450 Receiver 510 Auxiliary Condensing Eur
520 Auxiliary Evaporating Airflow 600 Indoor Heat Exchanger

Claims (15)

A compressor provided in the outdoor unit for compressing the refrigerant;
At least one indoor unit having an indoor heat exchanger in which a refrigerant discharged from the compressor is selectively guided, and disposed at a lower position than the outdoor unit;
An outdoor heat exchanger for selectively guiding the refrigerant discharged from the compressor; And
And an accumulator provided at the front end of the compressor in the outdoor unit and configured to supply only gaseous refrigerant to the compressor,
Wherein in the heating mode, the refrigerant condensed in the indoor heat exchanger is condensed through the auxiliary condensing flow passage before passing through the first main expansion valve in the front end of the outdoor heat exchanger. The method according to claim 1,
Further comprising a first branch flow channel and a second branch flow channel for branching the refrigerant flowing into the outdoor unit after being condensed in the indoor unit,
A part of the refrigerant flowing into the outdoor unit is guided to the auxiliary condensing flow passage through the first branch flow passage,
And the remainder of the refrigerant flowing into the outdoor unit is guided to the receiver provided at the lower end of the accumulator through the second branch flow channel. 3. The method of claim 2,
Further comprising an auxiliary evaporation flow path for heat exchange with the auxiliary condensation flow path,
And the liquid refrigerant in the receiver is guided to the auxiliary evaporation flow path. The method of claim 3,
And an auxiliary expansion valve is provided between the receiver and the auxiliary evaporation flow path. 5. The method of claim 4,
Wherein the first branch passage is provided with a first check valve formed in a direction toward the auxiliary condensing passage,
And a second check valve disposed between the receiver and the auxiliary expansion valve in a direction toward the auxiliary evaporation flow path. 5. The method of claim 4,
Wherein the refrigerant in the auxiliary condensing flow passage and the refrigerant in the auxiliary evaporation flow passage exchange heat with each other in the auxiliary heat exchange section. 3. The method of claim 2,
Wherein the first branch flow passage is provided with a first flow control valve and the second branch flow passage is provided with a second flow control valve,
Wherein the first flow rate regulating valve and the second flow rate regulating valve are adjusted in opening degree based on predetermined high pressure and predetermined subcooling degree. 5. The method of claim 4,
In the cooling mode, the refrigerant condensed in the outdoor heat exchanger is supercooled while passing through the auxiliary condensing duct of the auxiliary heat exchanger,
And a part of the refrigerant passing through the auxiliary condensing passage is branched and is guided to the accumulator after being evaporated while sequentially passing through the auxiliary expansion valve and the auxiliary evaporation passage. The method according to claim 1,
A receiver provided at the lower end of the accumulator and guided by the refrigerant condensed in the indoor heat exchanger;
A first branched flow path for guiding a part of the liquid refrigerant discharged from the receiver toward the outdoor heat exchanger; And
And a second branch flow path for guiding the remainder of the liquid refrigerant discharged from the receiver to the auxiliary evaporation flow path in the receiver. 10. The method of claim 9,
And an auxiliary expansion valve is provided at a front end of the auxiliary evaporation flow path. The method of claim 10, wherein
The accumulator and the receiver are integrally formed as a single case,
A partition plate is provided between the accumulator and the receiver, and the partition plate is formed of a thermally conductive member. 12. The method of claim 11,
A discharge port through which a discharge passage is connected is formed on a lower surface of the receiver,
An inlet port through which the refrigerant condensed in the indoor heat exchanger flows is formed on a side surface of the receiver,
Wherein the inlet port is closer to the partition plate than the lower surface of the receiver. 10. The method of claim 9,
An engine for driving the compressor;
A cooling water passage through which cooling water for cooling the engine flows;
Further comprising a plate heat exchanger for exchanging a part of the refrigerant guided toward the outdoor heat exchanger through the first branch flow channel with the cooling water. 14. The method of claim 13,
A third branch flow channel branched from the first branch flow channel toward the outdoor heat exchanger and a fourth branch flow channel branched toward the plate type heat exchanger,
Wherein the first main expansion valve is provided in the third branch flow passage and the second main expansion valve is provided in the fourth branch flow passage. 13. The method of claim 12,
In the cooling mode,
The refrigerant condensed in the outdoor heat exchanger is guided to the inlet of the receiver,
Wherein a part of the refrigerant discharged from the discharge port of the receiver and directed toward the indoor unit is guided to the auxiliary evaporation flow path through the second branch flow path to perform heat exchange with the refrigerant in the receiver.

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