KR101617394B1 - Refrigeration cycle system with multi heat exchanger - Google Patents

Abstract

The present invention provides a multi heat exchange refrigeration cycle system formed to remarkably reduce defrosting time and optimally maintaining the state of a refrigerant flowing into an evaporator. The multi heat exchange refrigeration cycle system includes: a compressor discharging a refrigerant of a gas state by compressing the refrigerant at a high temperature and a high pressure; a four-way valve connected to the compressor by a refrigerant flow path; a first heat exchanger connected to the four-way valve by the refrigerant flow path and exchanging the heat between the refrigerator and a heat source of the outside; a second heat exchanger connected to the first heat exchanger and the four-way valve by the refrigerant flow path and exchanging the heat between the refrigerant and the heat source of the outside; and a multi heat exchange unit installed on the refrigerant flow path connecting the first heat exchanger and the second heat exchanger and exchanging the heat between the refrigerants multiple times. The multi heat exchange unit exchanges the heat between the refrigerant flowing the refrigerant flow path connecting from the first heat exchanger to the second heat exchanger and the refrigerant discharged from the second heat exchanger and exchanges the heat between the refrigerant flowing in the refrigerant flow path connecting from the first heat exchanger to the second heat exchanger and the refrigerant flowing an eco flow path which is formed as the refrigerant connecting the first heat exchanger and the multi heat exchange unit flow path is diverged.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a multi-

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle system, and more particularly, to a refrigeration cycle system in which stability and efficiency are improved.

Generally, a heat pump means a device capable of moving heat from a low temperature to a high temperature. The configuration and operation of the cycle is the same as that of a freezer, but when it is intended to use only low temperature heat, it becomes a freezer And when it is intended to use high temperature heat, it becomes a heat pump.

The basic components of the heat pump cycle are divided into four components: a compressor, a first heat exchanger as a high temperature heat exchanger, an expansion valve, and a second heat exchanger as a low temperature heat exchanger. The refrigerant continues to undergo changes in compression, condensation, expansion, .

In the heat pump type heating apparatus capable of generating hot water for use in a bathroom or a factory using the principle of the heat pump described above, hot water can be obtained by exchanging heat between refrigerant and water introduced from the outside into the high temperature heat exchanger, The heating function can also be performed.

An example of such a heat pump system is disclosed in Korean Patent Registration No. 0913575.

During the operation of such a heat pump, changes in the condensation temperature or the evaporation temperature of the refrigerant occur due to various factors such as load variation, seasonal variation, scale of the cooling pipe, and the like, There is a problem that the compression ratio of the refrigerant increases, the temperature of the discharged gas increases, the refrigerating effect decreases, the coefficient of performance (COP) decreases, and the refrigerant circulation amount decreases due to the increase in specific volume of refrigerant. Such a problem lowers the performance of the heat pump system as a whole. In addition, when the defrosting operation time increases due to the decrease of the outside air temperature, the efficiency of the heat pump system deteriorates, and therefore, the defrosting operation time needs to be reduced.

SUMMARY OF THE INVENTION It is an object of the present invention to overcome the above-mentioned problems, and it is an object of the present invention to improve the refrigerant cycle of a refrigerant cycle of a heat pump system, And the defrosting time can be remarkably reduced.

In order to achieve the above object, a multi-heat exchange refrigeration cycle system according to an embodiment of the present invention includes: a compressor for compressing and discharging refrigerant in a gaseous state to high temperature and high pressure;

A four-way valve connected to the compressor through a refrigerant passage;

A first heat exchanger connected by the four-way valve and the refrigerant channel and performing heat exchange between the external heat source and the refrigerant;

A second heat exchanger connected to the first heat exchanger, the four-way valve, and the refrigerant channel and performing heat exchange between the external heat source and the refrigerant; And

And a multiple heat exchange unit disposed on a refrigerant flow path connecting the first heat exchanger and the second heat exchanger and performing heat exchange between the refrigerant plural times,

The multi-heat exchanging unit performs heat exchange between the refrigerant flowing in the refrigerant passage connecting the first heat exchanger and the second heat exchanger and the refrigerant discharged from the second heat exchanger, and the refrigerant discharged from the first heat exchanger to the second heat exchanger The heat exchange is performed between the refrigerant flowing through the refrigerant passage connected to the refrigerant passage and the refrigerant passage connecting the first heat exchanger and the multiple heat exchange unit to the refrigerant flowing through the echo passage formed by branching.

The first heat exchanger and the second heat exchanger may be air-cooled heat exchangers in which heat exchange is performed between air and refrigerant.

The first heat exchanger is a hot water heat exchanger in which heat exchange is performed between water and refrigerant,

The second heat exchanger may be an air-cooled heat exchanger for exchanging heat between air and refrigerant.

A hot water generating solenoid valve provided on a refrigerant passage connecting the compressor and the four-way valve; And

A hot water generating device which is disposed on a hot water generating flow path which is branched from a refrigerant flow path that flows from the compressor to the hot water generating solenoid valve and connects to the flow path connecting the hot water generating solenoid valve and the four- And a heat exchanger.

And a hot gas bypass flow path branched from a refrigerant flow path from the compressor to the four-way valve and connected to a flow path connecting the multiple heat exchange unit and the second heat exchanger.

In the multiple heat exchange refrigeration cycle system according to the present invention, the heat exchange between the refrigerants is performed at least twice in the multiple heat exchange units disposed on the flow path connecting the first heat exchanger and the second heat exchanger, so that the supercooling of the refrigerant flowing into the second heat exchanger And the temperature of the refrigerant flowing into the compressor is maintained at an optimal temperature, thereby reducing the power ratio, maintaining a stable cycle, and prolonging the service life of the system remarkably. Further, in the multi-heat exchange refrigeration cycle system according to the present invention, when the multiple heat exchange unit is used as an evaporator or a re-evaporator, a stable refrigeration cycle can be formed regardless of the temperature of the outside air, .

1 is a configuration diagram of a multiple heat exchange refrigeration cycle system for explaining a first embodiment of the present invention.
FIG. 2 is a view showing a flow of a refrigerant when the refrigeration cycle is operated in the system shown in FIG. 1. FIG.
Fig. 3 is a view showing the flow of the refrigerant when operating the defrost cycle in the system shown in Fig. 1. Fig.
4 is a configuration diagram of a multiple heat exchange refrigeration cycle system for explaining a second embodiment of the present invention.
5 is a view showing a flow of refrigerant when operating a heating cycle in the system shown in FIG.
FIG. 6 is a view showing the flow of the refrigerant when the cooling cycle is operated in the system shown in FIG. 4. FIG.
7 is a configuration diagram of a multi-heat exchange refrigeration cycle system for explaining a third embodiment of the present invention.
8 is a configuration diagram of a multiple heat exchange refrigeration cycle system for explaining a fourth embodiment of the present invention.
9 is a view showing the flow of the refrigerant when the heating cycle is operated in the system shown in Fig.
10 is a view showing a flow of refrigerant when the cooling cycle is operated in the system shown in FIG.

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

1 is a configuration diagram of a multiple heat exchange refrigeration cycle system for explaining a first embodiment of the present invention. FIG. 2 is a view showing a flow of a refrigerant when the refrigeration cycle is operated in the system shown in FIG. 1. FIG. Fig. 3 is a view showing the flow of the refrigerant when operating the defrost cycle in the system shown in Fig. 1. Fig. 4 is a configuration diagram of a multiple heat exchange refrigeration cycle system for explaining a second embodiment of the present invention. 5 is a view showing a flow of refrigerant when operating a heating cycle in the system shown in FIG. FIG. 6 is a view showing the flow of the refrigerant when the cooling cycle is operated in the system shown in FIG. 4. FIG. 7 is a configuration diagram of a multi-heat exchange refrigeration cycle system for explaining a third embodiment of the present invention. 8 is a configuration diagram of a multiple heat exchange refrigeration cycle system for explaining a fourth embodiment of the present invention. 9 is a view showing the flow of the refrigerant when the heating cycle is operated in the system shown in Fig. 10 is a view showing a flow of refrigerant when the cooling cycle is operated in the system shown in FIG.

1 to 3, a multiple heat exchange refrigeration cycle system 10 according to a first embodiment of the present invention includes a compressor 20, an oil separator 22, a four-way valve 30, A receiver 40, a receiver 50, a multiple heat exchange unit 60, and a second heat exchanger 80. [

The compressor (20) is a device for compressing gaseous refrigerant into high temperature and high pressure state. Only the gaseous refrigerant should flow into the compressor 20, and components of the compressor 20 may be damaged when the refrigerant in the liquid state flows into the compressor 20. Therefore, the oil separator 22 is installed in the refrigerant passage discharged from the compressor 20. The oil separator 22 recovers the oil separated from the refrigerant gas to the compressor 20. As the compressor 20, a ZF or ZFI compressor manufactured by Emerson-Copeland may be employed.

The four-way valve (30) is disposed on a flow path through which the refrigerant discharged from the compressor (20) passes. That is, the four-way valve 30 is connected to the compressor through a refrigerant passage. The four-way valve 30 is a valve device for branching the flow of the refrigerant in three directions. Since the four-way valve 30 may have a known structure, detailed description of the four-way valve 30 itself will be omitted.

The first heat exchanger (40) is connected to the four-way valve (30) by a refrigerant passage. The first heat exchanger (40) is a component that performs heat exchange between an external heat source and a refrigerant. The first heat exchanger (40) employs an air-cooled heat exchanger in which heat exchange is performed between air and refrigerant in the first embodiment.

The receiver (50) is connected to the first heat exchanger (40) by a refrigerant channel. The receiver (50) has a function of separating the refrigerant converted into the liquid state after the heat exchange in the first heat exchanger (40) and the gaseous refrigerant and discharging the refrigerant into the liquid heat exchanger (60) .

A first electromagnetic valve (42) is provided on a flow path connecting the first heat exchanger (40) and the receiver (50).

The second heat exchanger (80) is connected to the first heat exchanger (40) and the four-way valve (30) by a refrigerant passage. More specifically, the second heat exchanger (80) is connected to the first heat exchanger (40) by a refrigerant passage passing through the receiver (50) and the multiple heat exchanging unit (60) described later. The second heat exchanger (80) is a component that performs heat exchange between the external heat source and the refrigerant. The second heat exchanger (80) performs heat exchange between the external air heat source and the refrigerant.

The multiple heat exchange unit (60) is disposed on a refrigerant flow path connecting the first heat exchanger (40) and the second heat exchanger (80). More specifically, the multiple heat exchange unit (60) is disposed on a refrigerant passage connecting the receiver (50) and the second heat exchanger (80). In the multi-heat exchanging unit (60), the refrigerant heat exchange occurs a plurality of times. The multi-heat exchanging unit 60 is a component that implements the core operational effects of the present invention. The multi-heat exchanging unit 60 maintains optimal superheating degree or supercooling degree of the refrigerant flowing into the second heat exchanger 80 by causing heat exchange between the refrigerants, and the pressure of the refrigerant flowing into the compressor 20 So that it does not become too high.

A dryer 51 and a sight glass 52 are installed on the refrigerant channel connecting the receiver 50 and the multiple heat exchanging unit 60. The dryer 51 is a kind of filter for filtering foreign substances contained in the refrigerant. The sight glass 52 is a component that is installed to observe the flow of the fluid flowing through the refrigerant passage.

A first check valve (61) is installed on the refrigerant flow path connecting the multiple heat exchange unit (60) and the second heat exchanger (80). The first check valve 61 allows the refrigerant to flow from the multiple heat exchange unit 60 to the second heat exchanger 80 only. The refrigerant having passed through the first check valve 61 may be introduced into the second heat exchanger 80 through the second solenoid valve 62 and the first expansion valve 63. The first expansion valve (63) serves to thermally expand the liquid refrigerant to convert it into gaseous refrigerant. The flow path connecting the second heat exchanger (80) and the first check valve (61) is branched from the middle to constitute a bypass flow path bypassing the second solenoid valve (62) and the first expansion valve (63) And a second check valve 64 is provided on the bypass passage. The second check valve 64 allows the refrigerant to flow only from the second heat exchanger 80 toward the first check valve 61.

The refrigerant flow path connecting the multiple heat exchange unit 60 and the first check valve 61 branches and forms a flow path directly connected to the first heat exchanger 40. A third solenoid valve 65 And a second expansion valve 66 are provided.

The flow path connecting the first check valve 61 and the second check valve 64 is branched to be connected to a refrigerant flow path connecting the second solenoid valve 62 and the receiver 50, A fifth check valve (67) is provided on the refrigerant flow path. The fifth check valve 67 allows the refrigerant to flow from the second check valve 64 to the first heat exchanger 40 only. The fifth check valve 67 is opened during the defrost cycle operation and remains closed during the other cycles.

The refrigerant discharged from the second heat exchanger (80) flows into the compressor (20) through the four-way valve (30) after heat exchange is performed between the refrigerants in the multiple heat exchange unit (60). A third check valve 82 is installed on the refrigerant flow path which is discharged from the second heat exchanger 80 and is heat-exchanged in the multiple heat exchange unit 60 and then flows into the four-way valve 30. The third check valve 82 allows the refrigerant to flow from the multiple heat exchange unit 60 to the four-way valve 30 only. The refrigerant flow path connecting the third check valve 82 and the four-way valve 30 branches off to form a flow path that bypasses the multiple heat exchange unit 60 and is connected to the second heat exchanger 80, A fourth check valve 83 is provided on the flow path. The fourth check valve 83 allows the refrigerant to flow from the four-way valve 30 to the second heat exchanger 80 only.

The refrigerant branched from the channel connecting the site glass 52 and the multiple heat exchanging unit 60 forms an echo passage E1. The refrigerant flowing through the eco channel E1 is passed through the fourth solenoid valve 106, vaporized in the third expansion valve 105, and then introduced into the multiple heat exchange unit 60, And is sucked to the intermediate pressure of the compressor (20) in a state where the pressure is lowered. The refrigerant flowing through the echo passage E1 prevents the pressure of the refrigerant flowing into the compressor 20 from increasing excessively, thereby maintaining the optimum compressor performance.

The high-temperature and high-pressure refrigerant gas flowing into the four-way valve 30 from the oil separator 22 is branched before the four-way valve 30 and partially flows through the second expansion valve 66 and the third solenoid valve 65, The hot gas bypass flow path B1 is formed so as to be supplied to the flow path for connecting the hot gas bypass flow path B1. A fifth solenoid valve 108 is provided on the hot gas bypass passage B1. The hot gas bypass flow path B1 serves to adjust the degree of superheat of the refrigerant flowing into the second expansion valve 66 so as to cause the second expansion valve 66 to perform optimal thermal expansion.

That is, the multi-heat exchanging unit 60 is provided between the refrigerant flowing in the refrigerant passage connecting the first heat exchanger 40 and the second heat exchanger 80 and the refrigerant discharged from the second heat exchanger 80 And the refrigerant flowing through the refrigerant passage connecting the first heat exchanger (40) to the second heat exchanger (80) and the refrigerant flowing through the first heat exchanger (40) and the multiple heat exchange unit (60) And performs heat exchange between the refrigerant flowing through the eco-flow passage E1 formed by branching the flow-passage.

Hereinafter, the flow of the refrigerant will be described as an example of operating the refrigeration cycle and the defrost cycle in the system according to the first embodiment of the present invention.

Referring to FIG. 2, a case where the system according to the first embodiment of the present invention operates as a refrigeration cycle will be described in detail.

The refrigerant compressed in the compressor 20 at high temperature and high pressure passes through the oil separator 22, the four-way valve 30, and then flows into the first heat exchanger 40. In the first heat exchanger (40), the refrigerant undergoes heat exchange with an external air heat source, so that the temperature is lowered and a part of the refrigerant is converted into a liquid state. In this case, the first heat exchanger 40 serves as an air-cooling type condenser. The refrigerant having passed through the first heat exchanger (40) flows into the receiver (50) after passing through the first electromagnetic valve (42). In the receiver (50), only the circulating liquid refrigerant in the cycle is sent to the multiple heat exchange unit (60) through the dryer (51) and the sight glass (52). The refrigerant passing through the multiple heat exchanging unit 60 (D2 -> H2) passes through the first check valve 61 and the second solenoid valve 62 and flows into the first expansion valve 63 do. The refrigerant in the first expansion valve (63) is thermally expanded and converted into a gaseous state. The refrigerant discharged from the first expansion valve (63) flows into the second heat exchanger (80). In the second heat exchanger (80), the refrigerant receives heat from an external air heat source, and the temperature and the pressure increase. In this process, since the external air heat source deprives the refrigerant of heat, the temperature is lowered and the cooling effect of the specific space is realized. The second heat exchanger 80 performs cooling of the indoor space or refrigeration of the storage space. In this case, the second heat exchanger 80 functions as a unit cooler.

The refrigerant discharged from the second heat exchanger (80) flows into the multi-heat exchanging unit (60) and is heat-exchanged between the refrigerants. In this process, the liquid refrigerant flowing from the receiver (50) to the multi-heat exchanging unit (60) is lowered in temperature, and the refrigerant flowing from the second heat exchanger (80) to the multiple heat exchanging unit -> H3) The temperature of the gaseous refrigerant increases. Accordingly, the supercooling degree of the refrigerant flowing into the first expansion valve (63) from the multiple heat exchange unit (60) increases and the efficiency is improved. Further, the performance of the compressor 20 can be improved by increasing the degree of superheat of the refrigerant recovered from the multiple heat exchange unit 60 to the compressor 20 through the four-way valve 30. A part of the refrigerant flowing into the multiple heat exchange unit 60 from the receiver 50 is diverted and the refrigerant heat exchange D4 -> is performed in the multiple heat exchange unit 60 through the eco- D3) and sucked into the intermediate pressure of the compressor (20). After the refrigerant having passed through the eco-flow passage E1 is converted into a gaseous state from the third expansion valve 105, the degree of superheat is increased by the refrigerant heat exchange between the liquid and the gas in the multiple heat exchange unit 60, (20). The refrigerant passing through the echo passage E1 and sucked into the compressor 20 maintains the optimum temperature of the refrigerant flowing into the compressor 20, thereby preventing the compressor 20 from being overloaded.

Referring now to FIG. 3, the operation of the system according to the first embodiment of the present invention in a defrost cycle will be described in detail.

The refrigerant compressed at the high temperature and high pressure in the compressor 20 passes through the oil separator 22 and the four-way valve 30 and then flows through the fourth check valve 83 to the second heat exchanger 80 ≪ / RTI > When the second heat exchanger (80) is used as a unit cooler, the high-temperature and high-pressure refrigerant gas introduced from the compressor (20) exchanges heat with the gasses to remove the gasses. The refrigerant that has passed through the second heat exchanger 80 sequentially flows through the second check valve 64 and the fifth check valve 67 and flows into the receiver 50. In the receiver (50), only the circulating liquid refrigerant in the cycle is sent to the multiple heat exchange unit (60) through the dryer (51) and the sight glass (52). The refrigerant having passed through the multiple heat exchanging unit (60) is thermally expanded in the second expansion valve (66) through the third solenoid valve (65) and converted into a gaseous state. The refrigerant having passed through the second expansion valve (66) flows into the first heat exchanger (40). In the first heat exchanger (40), the external air heat source and the refrigerant undergo heat exchange so that the temperature of the refrigerant rises. In this case, the first heat exchanger 40 functions as a re-evaporator. The refrigerant discharged from the first heat exchanger (40) is recovered to the compressor (20) through the four-way valve (30). In this process, some high-temperature and high-pressure refrigerant gas introduced from the compressor (20) through the hot gas bypass flow path (B1) is mixed with liquid refrigerant flowing into the second expansion valve (66) Increase the temperature of the lowered refrigerant to a suitable state. As described above, the temperature of the refrigerant flowing into the second expansion valve (66) through the hot gas bypass flow path (B1) is appropriately maintained, so that the thermal expansion can smoothly occur. Thereby preventing the compressor (20) from being overloaded.

As described above, it is possible to prevent the compressor 20 from being overloaded through the multiple heat exchange unit 60 and the eco-flow passage E1 or the hot gas bypass flow passage B1, and to achieve the best refrigeration cycle or defrost cycle It is effective.

4 to 6, a multi-heat exchange refrigeration cycle system 10 according to a second embodiment of the present invention will now be described in detail.

The multiple heat exchange refrigeration cycle system 10 according to the second embodiment of the present invention is configured very similar to the first embodiment described with reference to Figs. Accordingly, only the constituent parts different from those of the first embodiment will be described below, and the description of the first embodiment will be referred to for the same constitution.

The multiple heat exchange refrigeration cycle system 10 according to the second embodiment includes the same compressor 20, oil separator 22, four-way valve 30, first heat exchanger 40, 50, a multiple heat exchange unit 60, and a second heat exchanger 80. The refrigerant circuit configuration between the compressor 20 and the first heat exchanger 40 is also the same as that of the first embodiment and the second embodiment. However, in the second embodiment, the first heat exchanger 40 is a hot water heat exchanger for exchanging heat between water and refrigerant, and the second heat exchanger 80 is an air-cooled heat exchanger for exchanging heat between air and refrigerant. As the first heat exchanger 40, for example, a plate heat exchanger may be employed.

The structure of the flow path connecting the first heat exchanger (40) and the receiver (50) is also the same as that of the first embodiment. Also, the flow path structure for connecting the receiver (50) and the multiple heat exchange unit (60) is the same as that of the first embodiment.

The circuit configuration for connecting the multiple heat exchange unit 60 and the second heat exchanger 80 is different from that of the first embodiment.

That is, a first check valve 61 is provided on the flow path connecting the multiple heat exchange unit 60 and the second heat exchanger 80, and has the same function as that of the first embodiment. On the other hand, a sixth check valve 71 is provided on the flow path connecting the first check valve 61 and the second heat exchanger 80, unlike the first embodiment. The sixth check valve 71 allows the refrigerant to flow from the first check valve 61 to the second heat exchanger 80 only. On the other hand, a second check valve (64) is provided as a flow path connecting the second heat exchanger (80) and the first check valve (61) on the flow passage bypassing the sixth check valve (71).

The refrigerant flow path connecting the multiple heat exchange unit 60 and the first check valve 61 branches and forms a flow path directly connected to the first heat exchanger 40. A third solenoid valve 65 And a second expansion valve 66 are provided.

The flow path connecting the first check valve 61 and the second check valve 64 is branched to be connected to a refrigerant flow path connecting the second solenoid valve 62 and the receiver 50, A fifth check valve (67) is provided on the refrigerant flow path. The fifth check valve 67 allows the refrigerant to flow from the second check valve 64 to the first heat exchanger 40 only.

The refrigerant discharged from the second heat exchanger (80) flows into the multiple heat exchange unit (60) through the second solenoid valve (62) and the first expansion valve (63). The refrigerant sequentially passed through the first expansion valve (63) and the multiple heat exchange unit (60) flows to the four-way valve (30). The refrigerant having passed through the four-way valve (30) is recovered by the compressor (20).

The flow path connecting the four-way valve 30 and the second heat exchanger 80 has a branched flow path bypassing the multiple heat exchange unit 60 and a fourth check valve 83 is provided on the flow path . The fourth check valve 83 allows the refrigerant to flow from the four-way valve 30 to the second heat exchanger 80 only.

The refrigerant branched from the channel connecting the site glass 52 and the multiple heat exchanging unit 60 forms an echo passage E1. The refrigerant flowing through the eco channel E1 is passed through the fourth solenoid valve 106, vaporized in the third expansion valve 105, and then introduced into the multiple heat exchange unit 60, And is sucked to the intermediate pressure of the compressor (20) in a state where the pressure is lowered. The refrigerant flowing through the echo passage E1 prevents the pressure of the refrigerant flowing into the compressor 20 from increasing excessively, thereby maintaining the optimum compressor performance.

The high-temperature and high-pressure refrigerant gas flowing into the four-way valve 30 from the oil separator 22 is branched before the four-way valve 30 and partially flows through the second expansion valve 66 and the third solenoid valve 65, The hot gas bypass flow path B1 is formed so as to be supplied to the flow path for connecting the hot gas bypass flow path B1. A fifth solenoid valve 108 is provided on the hot gas bypass passage B1. The hot gas bypass flow path B1 serves to adjust the degree of superheat of the refrigerant flowing into the second expansion valve 66 so as to cause the second expansion valve 66 to perform optimal thermal expansion.

That is, the multi-heat exchanging unit 60 is provided between the refrigerant flowing in the refrigerant passage connecting the first heat exchanger 40 and the second heat exchanger 80 and the refrigerant discharged from the second heat exchanger 80 And the refrigerant flowing through the refrigerant passage connecting the first heat exchanger (40) to the second heat exchanger (80) and the refrigerant flowing through the first heat exchanger (40) and the multiple heat exchange unit (60) And performs heat exchange between the refrigerant flowing through the eco-flow passage E1 formed by branching the flow-passage.

The high-temperature high-pressure refrigerant gas flowing into the four-way valve 30 from the oil separator 22 is branched before the four-way valve 30 so that a part of the refrigerant gas flows through the first expansion valve 63 and the second solenoid valve 62 are connected to the hot gas bypass flow path B1. A fifth solenoid valve 108 is provided on the hot gas bypass passage B1. The hot gas bypass flow path B1 serves to adjust the degree of superheat of the refrigerant flowing into the first expansion valve 63 so as to cause the first expansion valve 63 to achieve optimal thermal expansion.

The operation and effect of the present invention will be described while describing the flow of the refrigerant when the heating cycle and the cooling cycle operate in the multi-heat exchange refrigeration cycle system 10 according to the second embodiment.

A case where the system according to the second embodiment of the present invention operates in a heating cycle will be described in detail with reference to FIG.

  The refrigerant compressed in the compressor 20 at high temperature and high pressure passes through the oil separator 22, the four-way valve 30, and then flows into the first heat exchanger 40. In the first heat exchanger (40), the refrigerant undergoes heat exchange with water in the outside, thereby lowering the temperature and converting part of the refrigerant into a liquid state. In this case, the first heat exchanger 40 serves as a boiler for generating hot water for heating. The refrigerant having passed through the first heat exchanger (40) flows into the receiver (50) after passing through the first electromagnetic valve (42). In the receiver (50), only the circulating liquid refrigerant in the cycle is sent to the multiple heat exchange unit (60) through the dryer (51) and the sight glass (52). The refrigerant passing through the multiple heat exchanging unit 60 in the direction of D2 → H2 passes through the first check valve 61 and the sixth check valve 71 and flows into the second heat exchanger 80 do. In the second heat exchanger (80), the refrigerant receives heat from an external air heat source, and the temperature and the pressure increase. In this cycle, the second heat exchanger 80 functions as an evaporator as an outdoor unit.

The refrigerant discharged from the second heat exchanger (80) flows into the first expansion valve (63) through the second solenoid valve (62). The refrigerant in the first expansion valve (63) is thermally expanded and converted into a gaseous state. The refrigerant discharged from the first expansion valve (63) flows into the multiple heat exchange unit (60) and is heat-exchanged between the refrigerants. In this process, the liquid refrigerant flowing from the receiver (50) to the multi-heat exchanging unit (60) is lowered in temperature, and the refrigerant flowing from the second heat exchanger (80) The temperature and the pressure of the refrigerant increase. In this process ((H4 - > H3)), the multiple heat exchange unit 60 functions as a re-evaporator. Accordingly, the degree of superheat of the refrigerant recovered from the multiple heat exchange unit 60 to the compressor 20 through the four-way valve 30 increases, and the performance of the compressor 20 can be improved. A part of the refrigerant flowing into the multiple heat exchange unit 60 from the receiver 50 is branched and sucked to the intermediate pressure of the compressor 20 through the echo channel E1. After the refrigerant having passed through the eco-flow passage E1 is converted into a gaseous state from the third expansion valve 105, the degree of superheat is increased by the refrigerant heat exchange between the liquid and the gas in the multiple heat exchange unit 60, (20). The refrigerant passing through the echo passage E1 and sucked into the compressor 20 maintains the optimum temperature of the refrigerant flowing into the compressor 20, thereby preventing the compressor 20 from being overloaded. Alternatively, the refrigerant flowing into the first expansion valve (63) is mixed with the refrigerant gas of high temperature and high pressure through the hot gas bypass flow path (B1), so that the first expansion valve (63) You can make it happen.

Now, referring to FIG. 6, a case where the system according to the second embodiment of the present invention operates in a cooling cycle will be described in detail.

The refrigerant compressed at the high temperature and high pressure in the compressor 20 passes through the oil separator 22 and the four-way valve 30 and then flows through the fourth check valve 83 to the second heat exchanger 80 ≪ / RTI > The second heat exchanger (80) performs heat exchange between the low outside air and the refrigerant. In the second heat exchanger (80), the refrigerant is heat-exchanged with the external air heat source to lower the temperature and is converted into a liquid state. The refrigerant that has passed through the second heat exchanger 80 sequentially flows through the second check valve 64 and the fifth check valve 67 and flows into the receiver 50. In the receiver (50), only the circulating liquid refrigerant in the cycle is sent to the multiple heat exchange unit (60) through the dryer (51) and the sight glass (52). The refrigerant passing through the multiple heat exchanging unit 60 (D2 -> H2) is thermally expanded in the second expansion valve (66) through the third solenoid valve (65) and converted into a gaseous state. The refrigerant having passed through the second expansion valve (66) flows into the first heat exchanger (40). The first heat exchanger (40) performs heat exchange with water and the temperature of the refrigerant rises. In this case, the first heat exchanger 40 serves as an evaporator. In addition, the water discharged from the first heat exchanger (40) is drawn into the refrigerant to generate cold water. The cold water can be circulated in a specific space to cool the air. The refrigerant discharged from the first heat exchanger (40) is recovered to the compressor (20) through the four-way valve (30). In this process, the refrigerant flowing into the first expansion valve (63) is mixed with the refrigerant gas of high temperature and high pressure through the hot gas bypass flow path (B1) so that the first expansion valve (63) It is possible to make it happen smoothly.

7 is a configuration diagram of a multiple heat exchange refrigeration cycle system according to a third embodiment of the present invention. The system shown in Fig. 7 has the same configuration as that of the second embodiment shown in Fig. 4, and additionally includes a solenoid valve 92 for generating hot water and a hot water generating heat exchanger 90 . 7, the hot water generating solenoid valve 92 is installed on a refrigerant passage connecting the compressor 20 and the four-way valve 30. The hot water generating heat exchanger 90 is branched from a refrigerant passage that flows from the compressor 20 to the hot water generating solenoid valve 92 to connect the hot water generating solenoid valve 92 and the four- And is disposed on the hot water generation flow path W1 which is joined to the flow path. 7, the hot water generating solenoid valve 92 is locked so that the coolant for generating hot water flows from the compressor 20 via the oil separator 22 to the hot water generating flow path W1 disposed on the hot water generating flow path W1 And then flows into the heat exchanger (90). After the heat exchange between water and refrigerant occurs in the hot water generating heat exchanger (90), it flows into the first heat exchanger (40). A seventh check valve 94 is preferably provided on the hot water generating flow path W1. The seventh check valve 94 allows the refrigerant to flow from the hot water generating heat exchanger 90 only toward the four-way valve 30. The subsequent flow of the refrigerant can be configured so as to be greatly different from the heating cycle described with reference to Fig.

8 to 10, a multi-heat exchange refrigeration cycle system 10 according to a fourth embodiment of the present invention will now be described in detail.

The multiple heat exchange refrigeration cycle system 10 according to the fourth embodiment of the present invention is modified in the first embodiment described with reference to Figs. Accordingly, only the constituent elements different from those of the first embodiment will be described below, and the description of the first embodiment will be referred to for the same constitution.

The multiple heat exchange refrigeration cycle system 10 according to the fourth embodiment is similar to the first embodiment except that the compressor 20, the oil separator 22, the four-way valve 30, the first heat exchanger 40, (60), and a second heat exchanger (80). The refrigerant circuit structure between the compressor 20 and the first heat exchanger 40 is also the same as that of the first and fourth embodiments. In the fourth embodiment, both the first heat exchanger (40) and the second heat exchanger (80) are disposed indoors. That is, the multiple heat exchange refrigeration cycle system 10 according to the fourth embodiment can be applied to a movable heat pump system. The first heat exchanger (40) can function as a suction side heat exchanger.

The structure of the refrigerant passage connecting the first heat exchanger (40) and the multiple heat exchange unit (60) is different from that of the first embodiment. That is, the flow path connecting the first heat exchanger (40) and the multiple heat exchange unit (60) is branched from the middle into two and then joined again. The first check valve 61 is provided in one branched flow path. The first check valve 61 allows refrigerant to flow from the first heat exchanger 40 to the multiple heat exchange unit 60 only. On the other hand, a first expansion valve (63) and a second solenoid valve (62) are sequentially installed on the branched flow paths.

The refrigerant flow path connecting the first check valve 61 and the multiple heat exchanging unit 60 is branched into the multiple heat exchanging unit 60 and then introduced into the eco-flow passage E1 ). The eco channel E1 includes an expansion valve (not shown) for converting the liquid refrigerant into a gas. The refrigerant flowing through the echo passage E1 prevents the pressure of the refrigerant flowing into the compressor 20 from increasing excessively, thereby maintaining the optimum compressor performance.

The refrigerant flow from the first heat exchanger (40) through the multiple heat exchange unit (60) is connected to the second heat exchanger (80). A dryer 51 and a sight glass 52 may be installed on the flow path connecting the multiple heat exchange unit 60 and the second heat exchanger 80.

In the second heat exchanger (80), heat exchange occurs between the air and the refrigerant, and the temperature of the refrigerant rises. In this case, the second heat exchanger 80 may function as a discharge-side heat exchanger. The refrigerant discharged from the second heat exchanger (80) flows along a refrigerant flow path to the multiple heat exchange unit (60). A third solenoid valve (65) and a second expansion valve (66) are sequentially installed on the refrigerant flow path through which the refrigerant discharged from the second heat exchanger (80) flows into the multiple heat exchange unit (60). The refrigerant flow from the second expansion valve (66) through the multiple heat exchange unit (60) is connected to the compressor (20) via the four-way valve (30). The flow path connecting the four-way valve 30 and the second heat exchanger 80 is connected to the multiple heat exchanging unit 60 and the branch which bypasses the second expansion valve 66 and the third solenoid valve 65 And a fourth check valve 83 is provided on the flow path. The fourth check valve 83 allows the refrigerant to flow from the four-way valve 30 to the second heat exchanger 80 only.

The high-temperature and high-pressure refrigerant gas flowing into the four-way valve 30 from the oil separator 22 is branched before the four-way valve 30 and partially flows through the second expansion valve 66 and the third solenoid valve 65, The hot gas bypass flow path B1 is formed so as to be supplied to the flow path for connecting the hot gas bypass flow path B1. A fifth solenoid valve 108 is provided on the hot gas bypass passage B1. The hot gas bypass flow path B1 serves to adjust the degree of superheat of the refrigerant flowing into the second expansion valve 66 so as to cause the second expansion valve 66 to perform optimal thermal expansion.

The operation and effect of the present invention will be described while describing the flow of the refrigerant when the heating cycle and the cooling cycle operate in the multi-heat exchange refrigeration cycle system 10 according to the fourth embodiment configured as described above.

Referring to FIG. 9, a case where the system according to the fourth embodiment of the present invention operates in a heating cycle will be described in detail.

The refrigerant compressed in the compressor 20 at high temperature and high pressure passes through the oil separator 22, the four-way valve 30, and then flows into the first heat exchanger 40. In the first heat exchanger (40), the refrigerant undergoes heat exchange with air, thereby lowering the temperature and converting part of the refrigerant into a liquid state. The refrigerant having passed through the first heat exchanger (40) passes through the first check valve (61) and then flows into the multiple heat exchange unit (60). The refrigerant passing through the multiple heat exchanging unit 60 in the direction of H2 -> D2 flows into the second heat exchanger 80 through the dryer 51 and the sight glass 52. In the second heat exchanger (80), the refrigerant receives heat from an air heat source in a specific room, and the temperature and the pressure increase. In this process, since the air heat source deprives the refrigerant of heat, the temperature is lowered and the cooling effect of the specific space is realized. The second heat exchanger 80 performs cooling of the indoor space or refrigeration of the storage space.

The refrigerant discharged from the second heat exchanger (80) flows into the second expansion valve (66) via the third solenoid valve (65). The refrigerant in the second expansion valve (66) is thermally expanded to be converted into a gaseous state. The refrigerant discharged from the second expansion valve (66) flows into the multiple heat exchanging unit (60) in the direction of D4 - > D3 to perform heat exchange between the refrigerants. In this process, the temperature of the gaseous refrigerant flowing from the second heat exchanger (80) to the multiple heat exchange unit (60) increases. In this process ((H4 - > D3)), the multiple heat exchange unit 60 functions as an evaporator. Accordingly, the multi-heat exchanging unit 60 serving as an evaporator performs an evaporator regardless of the outside air temperature. That is, in the fourth embodiment, since the heat exchanging unit 60 does not perform heat exchange with the outside air, the homeostasis can be maintained in view of performance. The refrigerant having passed through the multiple heat exchanging unit (60) from the second expansion valve (66) is recovered to the compressor (20) via the four-way valve (30). In this process, the multi-heat exchanging unit 60 performs heat exchange between the liquid and the gaseous refrigerant, thereby enabling a stable heating cycle regardless of the external environment.

If necessary, the refrigerant discharged from the first heat exchanger 40 flows through the first check valve 61 and then flows into the multiple heat exchanging unit 60 through the echo passage E1, The refrigerant can be directly sucked into the compressor 20 after the superheat degree is increased.

10, the operation of the system according to the fourth embodiment of the present invention in a cooling cycle will be described in detail.

The refrigerant compressed at the high temperature and high pressure in the compressor 20 passes through the oil separator 22 and the four-way valve 30 and then flows through the fourth check valve 83 to the second heat exchanger 80 ≪ / RTI > The second heat exchanger (80) performs heat exchange between air and refrigerant. In the second heat exchanger (80), the refrigerant is heat-exchanged with the air heat source to lower the temperature and is converted into a liquid state. The refrigerant having passed through the second heat exchanger (80) passes through the sight glass (52) and the dryer (51) and flows into the multiple heat exchange unit (60). The refrigerant passing through the multiple heat exchange unit 60 (D2 -> H2) is thermally expanded in the first expansion valve (63) through the second solenoid valve (62) and converted into a gaseous state. The refrigerant having passed through the first expansion valve (63) flows into the first heat exchanger (40). Heat exchange is performed between air and refrigerant in the first heat exchanger (40) and the temperature of the refrigerant rises. In this case, the first heat exchanger 40 serves as an evaporator. In addition, the heat-exchanged air in the first heat exchanger (40) is heated by the refrigerant to cool a specific space. The refrigerant discharged from the first heat exchanger (40) is recovered to the compressor (20) through the four-way valve (30).

As described above, in the multi-heat exchange refrigeration cycle system according to the present invention, heat exchange between the refrigerants is performed at least twice in the multiple heat exchange units disposed on the flow path connecting the first heat exchanger and the second heat exchanger, The supercooling degree or the superheating degree of the refrigerant can be optimally maintained to increase the refrigerating effect and the temperature of the refrigerant flowing into the compressor can be maintained at an optimum temperature to thereby reduce the power ratio and maintain a stable cycle, Effect. Further, in the multi-heat exchange refrigeration cycle system according to the present invention, when the multiple heat exchange unit is used as an evaporator or a re-evaporator, a stable refrigeration cycle can be formed regardless of the temperature of the outside air, .

In particular, the multi-heat exchange refrigeration cycle system according to the present invention is effective for refrigeration and refrigeration systems for a low temperature showcase such as a supermarket, and can be ideally applied when the evaporation temperature of the refrigerant is below -15 ° C and the outside air temperature is below -15 ° C .

While the present invention has been shown and described with reference to certain preferred embodiments thereof, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, It is clear that this is possible.

10: Multiple heat exchange refrigeration cycle system
20: Compressor
22: Oil separator
30: Four way valve
40: first heat exchanger
42: first solenoid valve
50: Receiver
51: Dryer
52: Sight glass
60: Multiple heat exchange unit
61: first check valve
62: second solenoid valve
63: first expansion valve
65: third solenoid valve
66: second expansion valve
64: second check valve
67: fifth check valve
71: the sixth check valve
80: second heat exchanger
82: Third check valve
83: Fourth check valve
90: Hot water generating heat exchanger
92: Solenoid valve for generating hot water
94: Seventh check valve
105: third expansion valve
106: fourth solenoid valve
108: fifth solenoid valve
B1: Hot gas bypass oil line
E1: Echo Euro
W1: Hot water generating flow path

Claims (5)

A compressor for compressing and discharging gaseous refrigerant at a high temperature and a high pressure;
A four-way valve connected to the compressor through a refrigerant passage;
A first heat exchanger connected by the four-way valve and the refrigerant channel and performing heat exchange between the external heat source and the refrigerant;
A second heat exchanger connected to the first heat exchanger, the four-way valve, and the refrigerant channel and performing heat exchange between the external heat source and the refrigerant; And
And a multiple heat exchange unit disposed on a refrigerant flow path connecting the first heat exchanger and the second heat exchanger and performing heat exchange between the refrigerant plural times,
The multi-heat exchanging unit performs heat exchange between the refrigerant flowing in the refrigerant passage connecting the first heat exchanger and the second heat exchanger and the refrigerant discharged from the second heat exchanger, and the refrigerant discharged from the first heat exchanger to the second heat exchanger And performs heat exchange between the refrigerant flowing through the refrigerant channel and the refrigerant channel connecting the first heat exchanger and the multiple heat exchanging unit to the refrigerant flowing through the echo channel formed by branching,
A third check valve is provided on a refrigerant flow path which is discharged from the second heat exchanger and is heat-exchanged in the multiple heat exchange unit and then flows into the four-way valve,
The third check valve allows refrigerant to flow from the multiple heat exchange unit only to the four-way valve,
The refrigerant flow path connecting the third check valve and the four-way valve branches off to form a flow path that bypasses the multiple heat exchange units and is connected to the second heat exchanger, a fourth check valve is provided on the flow path,
And the fourth check valve permits the refrigerant to flow only from the four-way valve to the second heat exchanger. The method according to claim 1,
Wherein the first heat exchanger and the second heat exchanger are air-cooled heat exchangers in which heat exchange is performed between air and refrigerant. The method according to claim 1,
The first heat exchanger is a hot water heat exchanger in which heat exchange is performed between water and refrigerant,
Wherein the second heat exchanger is an air-cooled heat exchanger that performs heat exchange between air and refrigerant. The method according to claim 1,
A hot water generating solenoid valve provided on a refrigerant passage connecting the compressor and the four-way valve; And
A hot water generating device which is disposed on a hot water generating flow path which is branched from a refrigerant flow path that flows from the compressor to the hot water generating solenoid valve and connects to the flow path connecting the hot water generating solenoid valve and the four- And a heat exchanger. The method according to claim 1,
And a hot gas bypass flow path branched from a refrigerant flow path from the compressor to the four-way valve and connected to a flow path connecting the multiple heat exchange unit and the second heat exchanger.

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