Refrigerant system

Abstract

The present application discloses a refrigerant system, comprising a compressor, a first heat exchanger and a second heat exchanger which are communicated with the compressor, and a control device. The compressor is provided with an air discharge port; the first heat exchanger comprises a first heat exchange part and a second heat exchange part; the first heat exchange part and the second heat exchange part are each provided with a refrigerant flow path and a water path for heat exchange; the control device can control the refrigerant system to switch between a first mode and a second mode; in the first mode, a refrigerant circuit is formed among the compressor, the first heat exchange part, and the second heat exchanger, and a refrigerant circuit is formed among the compressor, the second heat exchange part, and the second heat exchanger; in the second mode, a refrigerant circuit is formed among the compressor, the second heat exchanger, and the first heat exchange part, and a refrigerant circuit is formed among the compressor, the second heat exchange part, and the first heat exchange part.

Description

Refrigerant system

[0001] Related applications

[0002] This application claims priority to Chinese patent application No. 202311718852.X filed on December 13, 2023, the entire contents of which are incorporated by reference into this application. Technical Field

[0003] The present application relates to the technical field of heat pumps, and in particular to a refrigerant system. Background Art

[0004] When the refrigerant system is heating at low temperatures, the outdoor heat exchanger is prone to ice and frost. Once the outdoor heat exchanger is frosted, the heat exchange efficiency will drop sharply, seriously affecting the heat exchange effect. Therefore, when the refrigerant system has been running in a low-temperature environment for a period of time or when the outdoor heat exchanger is severely frosted, it will generally enter the defrost mode to remove the frost on the outdoor heat exchanger.

[0005] The defrosting method of the existing refrigerant system is to switch the refrigerant system from heating mode to cooling mode for defrosting, that is, the compressor is stopped and the refrigerant circuit is reversed, resulting in discontinuous heating, thereby affecting user comfort.

[0006] Summary of the Invention

[0007] The main purpose of this application is to provide a refrigerant system, which aims to enable the refrigerant system to defrost without stopping the compressor, thereby maintaining continuous heating and improving user comfort.

[0008] To achieve the above objectives, the refrigerant system proposed in this application includes:

[0009] a compressor having an exhaust port;

[0010] a first heat exchanger and a second heat exchanger in communication with the compressor, wherein the first heat exchanger includes a first heat exchange portion and a second heat exchange portion, wherein the first heat exchange portion and the second heat exchange portion are provided with a refrigerant flow path and a water path for heat exchange; and

[0011] A control device, wherein the control device is capable of controlling the refrigerant system to switch between a first mode and a second mode, wherein in the first mode, a refrigerant circuit is formed between the compressor and the first heat exchange part and the second heat exchanger, and a refrigerant circuit is formed between the compressor and the second heat exchange part and the second heat exchanger; and in the second mode, a refrigerant circuit is formed between the compressor and the second heat exchange part and the first heat exchange part, and a refrigerant circuit is formed between the compressor and the second heat exchange part and the first heat exchange part.

[0012] In one embodiment, the compressor further has a return air port, the control device includes a four-way reversing valve, the first end of the second heat exchange part is connected to the exhaust port, the first interface of the four-way reversing valve is connected to the first end of the first heat exchange part, the second interface of the four-way reversing valve is connected to the second end of the second heat exchanger, the third interface of the four-way reversing valve is connected to the exhaust port, the fourth interface of the four-way reversing valve is connected to the return air port, and the first end of the second heat exchanger is connected to the second end of the first heat exchange part and the second end of the second heat exchange part.

[0013] In one embodiment, the refrigerant system further includes a first throttling device, wherein the first end of the first throttling device is connected to the second end of the first heat exchange part and the second end of the second heat exchange part, and the second end of the first throttling device is connected to the first end of the second heat exchanger.

[0014] In one embodiment, the exhaust port includes a first exhaust port and a second exhaust port, the first exhaust port is connected to the third port of the four-way reversing valve, and the second exhaust port is connected to the first end of the second heat exchange part.

[0015] In one embodiment, the refrigerant system also includes a second throttling device, the first end of the second throttling device is connected to the second end of the first heat exchange part and the second heat exchange part, where the refrigerant pressure is larger in the first mode, and the second end of the second throttling device is connected to the first end of the first throttling device.

[0016] In one embodiment, the refrigerant pressure of the first exhaust port is higher than the refrigerant pressure of the second exhaust port, and the second end of the second heat exchange portion is connected to the first end of the first throttling device.

[0017] In one embodiment, the refrigerant pressure of the first exhaust port is lower than the refrigerant pressure of the second exhaust port, and the refrigerant system further includes a fourth throttling device, and the second end of the first heat exchange part is connected to the first end of the first throttling device through the fourth throttling device.

[0018] In one embodiment, the exhaust port is configured as one, and the refrigerant system also includes a diverter pipe, the diverter pipe having two connected diverter outlets, the air inlet of the diverter pipe is connected to the exhaust port, one of the diverter outlets is connected to the third interface of the four-way reversing valve, and the other diverter outlet is connected to the first end of the second heat exchange part.

[0019] In one embodiment, the refrigerant system further includes a second throttling device, wherein a first end of the second throttling device is connected to the second end of the first heat exchange portion, and a second end of the second throttling device is connected to the first end of the first throttling device.

[0020] In one embodiment, the refrigerant system also includes an economizer, an air supply pipeline and a third throttling device. The economizer is provided with a third refrigerant flow path and a fourth refrigerant flow path for phase heat exchange. The first end of the third refrigerant flow path is connected to the second end of the first heat exchange part and the second end of the second heat exchange part. The first end of the second heat exchanger is connected to the second end of the third refrigerant flow path and the first end of the fourth refrigerant flow path. The second end of the fourth refrigerant flow path is connected to the air supply port of the compressor through the air supply pipeline.

[0021] In one embodiment, the first end of the second throttling device is connected to the second end of the first heat exchange portion, and the second end of the second throttling device is connected to the first end of the third refrigerant flow path.

[0022] In one embodiment, the first heat exchange portion and the second heat exchange portion are disposed adjacent to each other.

[0023] In one embodiment, the first heat exchange portion and the second heat exchange portion are integrated into a same first heat exchanger.

[0024] In one embodiment, the first heat exchanger is configured as a plate heat exchanger and is provided with a refrigerant flow path and a water path for heat exchange, the refrigerant flow path includes a first refrigerant flow path and a second refrigerant flow path, the water path includes a first water path corresponding to the first refrigerant flow path, and a second water path corresponding to the second refrigerant flow path, the water path is provided with a water inlet, a first water outlet corresponding to the first water path, and a second water outlet corresponding to the second water path.

[0025] In one embodiment, the water inlet is connected to both the first water path and the second water path, and the pressures of the refrigerants flowing through the first refrigerant flow path and the second refrigerant flow path are configured to be different, so that the outlet water temperatures of the first water outlet and the second water outlet are different.

[0026] In one embodiment, the water inlet is communicated with the first water channel, and the first water channel and the second water channel are connected in series, so that the outlet water temperatures of the first water outlet and the second water outlet are different.

[0027] In one embodiment, a flow valve is provided on the first water outlet and / or the second water outlet to adjust the water flow rate of the first water outlet and the second water outlet.

[0028] In the technical solution of the present application, a control device is used to enable the refrigerant system to defrost the second heat exchanger in the second mode without stopping the compressor and without interrupting the heating of the first heat exchanger. This not only ensures continuous and stable heating to improve user comfort, but also reduces the risk of failure caused by frequent start-stop of major electrical components such as the compressor, thereby extending the service life of the compressor and the refrigerant system. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0030] FIG1 is a schematic diagram of a refrigerant circuit of a first embodiment of a refrigerant system of the present application in a first mode;

[0031] FIG2 is a schematic diagram of a refrigerant circuit of the refrigerant system shown in FIG1 in a second mode;

[0032] FIG3 is a schematic diagram of a refrigerant circuit of a second embodiment of the refrigerant system of the present application in a first mode;

[0033] FIG4 is a schematic diagram of a refrigerant circuit of the refrigerant system shown in FIG3 in a second mode;

[0034] FIG5 is a schematic diagram of a refrigerant circuit of a third embodiment of the refrigerant system of the present application in the first mode;

[0035] FIG6 is a schematic diagram of a refrigerant circuit in the first mode of the fourth embodiment of the refrigerant system of the present application;

[0036] FIG7 is a schematic diagram of a refrigerant circuit of the refrigerant system shown in FIG6 in the second mode;

[0037] FIG8 is a schematic diagram of a refrigerant circuit in the first mode of the fifth embodiment of the refrigerant system of the present application;

[0038] FIG9 is a schematic diagram of a refrigerant circuit of the refrigerant system shown in FIG8 in the second mode;

[0039] FIG10 is a schematic diagram of a refrigerant circuit in the first mode of the sixth embodiment of the refrigerant system of the present application;

[0040] FIG11 is a schematic diagram of a refrigerant circuit of the refrigerant system shown in FIG10 in the second mode;

[0041] FIG12 is a schematic diagram of a refrigerant circuit in the first mode of the seventh embodiment of the refrigerant system of the present application;

[0042] FIG13 is a schematic diagram of a refrigerant circuit of the refrigerant system shown in FIG12 in the second mode;

[0043] FIG14 is a schematic structural diagram of an embodiment of the first heat exchanger of the present application;

[0044] FIG15 is a schematic structural diagram of another embodiment of the first heat exchanger of the present application;

[0045] FIG16 is a schematic structural diagram of an embodiment of a plate heat exchanger of the present application;

[0046] FIG17 is a schematic diagram of the partial structure of another embodiment of the plate heat exchanger of the present application at point A shown in FIG16 ;

[0047] FIG18 is a schematic diagram of the waterway flow direction of the embodiment shown in FIG16 ;

[0048] FIG19 is a schematic diagram of the water flow direction of another embodiment of the plate heat exchanger of the present application;

[0049] FIG20 is a schematic diagram of the water flow direction of a plate heat exchanger according to another embodiment of the present application;

[0050] FIG21 is a schematic structural diagram of the eighth embodiment of the refrigerant system of the present application.

[0051] Description of Figure Numbers:

[0052] The realization of the objectives, functional features and advantages of this application will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0053] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0054] It should be noted that if the embodiments of the present application involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the various components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indications will also change accordingly.

[0055] In this application, unless otherwise specified or limited, the terms "connection" and "fixation" should be understood in a broad sense. For example, "fixation" can mean fixed connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; internal communication between two elements or interaction between two elements, unless otherwise specified. For those skilled in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0056] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present application, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or suggesting their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of such features. In addition, the meaning of "and / or" appearing throughout the text includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme in which A and B are satisfied at the same time. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement it. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by this application.

[0057] This application proposes a refrigerant system, including but not limited to an air conditioner and a heat pump device, wherein the heat pump device includes but is not limited to an ATW (Air-Water) heat pump device and an ATA (Air-Air) heat pump device. Please refer to Figures 1 to 13, which are schematic diagrams of the refrigerant circuits of different embodiments of the refrigerant system of this application in the first mode or the second mode. The hollow arrows in the figures indicate the flow direction of air and / or water used for heat exchange with the first heat exchanger.

[0058] Please refer to Figures 1 to 13. In some embodiments of the present application, the refrigerant system includes a compressor 20, a first heat exchanger 10 and a second heat exchanger 40 that are connected to each other. The first heat exchanger 10 includes a first heat exchange part 10a and a second heat exchange part 10b. The compressor 20 has an exhaust port and a return air port 203. The exhaust port of the compressor is connected to the first end of the first heat exchange part 10a and the first end of the second heat exchange part 10b. The first end of the second heat exchanger 40 is connected to the second end of the first heat exchange part 10a and the second end of the second heat exchange part 10b. The second end of the second heat exchanger 40 is connected to the return air port 203.

[0059] In some embodiments, the first heat exchange unit 10a and the second heat exchange unit 10b are provided with a refrigerant flow path and a water path for heat exchange. The water in the water path is heated by heat exchange with the refrigerant in the refrigerant flow path, and the heated water can be used as heating hot water and / or domestic hot water, thereby heating and / or providing hot water to the indoor space. Of course, in other embodiments, the first heat exchange unit 10a and the second heat exchange unit 10b can also be provided with only the refrigerant flow path.

[0060] In some embodiments, the refrigerant system also includes a control device 80, which is capable of controlling the refrigerant system to switch between a first mode and a second mode. In the first mode, a refrigerant circuit is formed between the compressor and the first heat exchange part 10a and the second heat exchanger 40, and a refrigerant circuit is formed between the compressor and the second heat exchange part 10b and the second heat exchanger 40; in the second mode, a refrigerant circuit is formed between the compressor 20 and the second heat exchanger 40 and the first heat exchange part 10a, and a refrigerant circuit is formed between the compressor 20 and the second heat exchanger 40 and the first heat exchange part 10a.

[0061] Specifically, in the first mode, a portion of the refrigerant flowing out of the exhaust port passes through the first heat exchange part 10a and the second heat exchanger 40 in sequence and returns to the compressor 20, and another portion of the refrigerant flowing out of the exhaust port passes through the second heat exchange part 10b and the second heat exchanger 40 in sequence and returns to the compressor 20; in the second mode, a portion of the refrigerant flowing out of the exhaust port passes through the second heat exchanger 40 and the first heat exchange part 10a in sequence and returns to the compressor 20, and another portion of the refrigerant flowing out of the exhaust port passes through the second heat exchange part 10b and the first heat exchange part 10a in sequence and returns to the compressor 20.

[0062] In this embodiment, in the first mode, the control device 80 controls the flow direction of the refrigerant so that the refrigerant flowing out of the compressor 20 first flows to the first heat exchange section 10a and the second heat exchange section 10b, and then flows to the second heat exchanger 40. At this time, the first heat exchange section 10a and the second heat exchange section 10b both serve as condensers, and the second heat exchanger 40 serves as an evaporator, thereby forming a refrigerant heating circuit. In the second mode, the control device 80 controls the flow direction of the refrigerant so that the second heat exchanger 40 is converted into a condenser. At the same time, one of the first heat exchange section 10a and the second heat exchange section 10b continues to serve as a condenser, while the other is converted into an evaporator, thereby forming a new refrigerant heating circuit. In this way, a portion of the refrigerant flowing out of the exhaust port can maintain the continuity of heating and improve user comfort, while the other portion of the refrigerant is used to cause the second heat exchanger 40 to self-heat and melt frost on its surface.

[0063] It should be noted that when the refrigerant system is configured as an air conditioner, the first heat exchanger is used to exchange heat with the air in the indoor space. It can be set as a whole in the indoor space, as a whole in the outdoor space, or partly in the indoor space and the other part in the outdoor space. That is, this application does not make specific restrictions on the layout position of the first heat exchanger; similarly, this application does not make specific restrictions on the layout position of the second heat exchanger.

[0064] In the technical solution of the present application, the control device 80 is used to enable the refrigerant system to defrost the second heat exchanger 40 in the second mode without stopping the compressor 20 and without interrupting the heating supply of the first heat exchanger. This not only ensures continuous and stable heating to improve user comfort, but also reduces the risk of failure caused by frequent start-stop of major electrical components such as the compressor 20, thereby increasing the service life of the compressor 20 and the refrigerant system.

[0065] Referring to Figures 1 and 2, in one embodiment, the control device 80 is configured as a single four-way reversing valve 81. The first end of the second heat exchange portion 10b is connected to the exhaust port, the E port (i.e., the first port) of the four-way reversing valve 81 is connected to the first end of the first heat exchange portion 10a, the C port (i.e., the second port) of the four-way reversing valve 81 is connected to the second end of the second heat exchanger 40, the D port (i.e., the third port) of the four-way reversing valve 81 is connected to the exhaust port, and the S port (i.e., the fourth port) of the four-way reversing valve 81 is connected to the return air port 203. The first end of the second heat exchanger 40 is connected to the second end of the first heat exchange portion 10a and the second end of the second heat exchange portion 10b. In this way, the single four-way reversing valve 81 can achieve the non-stop defrosting function of the refrigerant system's compressor 20. This simple and easy-to-implement structure can significantly reduce the production and maintenance costs of the refrigerant system.

[0066] Specifically, in this embodiment, in the first mode, a single four-way reversing valve 81 controls the flow of the refrigerant, causing the refrigerant flowing from the compressor 20 to first flow to the first heat exchange section 10a and the second heat exchange section 10b, and then to the second heat exchanger 40. At this time, the first heat exchange section 10a and the second heat exchange section 10b both function as condensers, and the second heat exchanger 40 functions as an evaporator, thereby forming a refrigerant heating circuit. In the second mode, the four-way reversing valve 81 controls the flow of the refrigerant, causing the second heat exchanger 40 to function as a condenser, while the second heat exchange section 10b continues to function as a condenser and the first heat exchange section 10a to function as an evaporator, thereby forming a new refrigerant heating circuit. This allows a portion of the refrigerant to remain used for heating the indoor space, while the remaining portion is used to generate self-heating heat in the second heat exchanger 40 to melt frost on its surface.

[0067] It's worth noting that when the refrigerant system is configured as an air conditioner or ATA heat pump, and is equipped with a single four-way reversing valve 81, the second mode can also function as a dehumidification mode. This means both modes are available to the user, allowing them to select either mode based on their needs. Specifically, during the cold winter months, the second mode is used to convert the second heat exchanger 40 into a condenser to remove frost from its surface. During the rainy season, the dehumidification mode is used to convert the first heat exchange unit 10a into an evaporator to absorb heat and dehumidify the indoor air. The dehumidified air is then heated by the second heat exchange unit 10b, acting as a condenser. This provides dry, warm air to the indoor space and prevents significant fluctuations in indoor temperature.

[0068] Referring to Figure 5, in another embodiment, the control device 80 may also include a four-way reversing valve 81 and a solenoid valve 82. The first end of the second heat exchange part 10b is connected to the exhaust port through the solenoid valve 82, the E interface of the four-way reversing valve 81 is connected to the first end of the first heat exchange part 10a, the C interface of the four-way reversing valve 81 is connected to the second end of the second heat exchanger 40, the D interface of the four-way reversing valve 81 is connected to the exhaust port, and the S interface of the four-way reversing valve 81 is connected to the return air port 203. The first end of the second heat exchanger 40 is connected to the second end of the first heat exchange part 10a and the second end of the second heat exchange part 10b. In this way, when the refrigerant system enters the first mode and the second mode, the solenoid valve 82 is opened to connect the second heat exchange part 10b and the second exhaust port 202; when the refrigerant system enters the cooling mode, the solenoid valve 82 is closed to cut off the second heat exchange part 10b and the second exhaust port 202, and stop the second heat exchange part 10b from working, thereby preventing the second heat exchange part 10b from being converted into a condenser and affecting the cooling effect of the first heat exchange part 10a on the indoor air.

[0069] Of course, the control device 80 can also adopt other structural forms, such as a control valve group composed of multiple control valves, as long as it can control the switching of the refrigerant flow direction to achieve switching between the first mode and the second mode. This application does not limit this.

[0070] Referring to Figures 1 to 9 , in some embodiments, the exhaust port includes a first exhaust port 201 and a second exhaust port 202. The first exhaust port 201 is connected to the D port of the four-way reversing valve 81, and the second exhaust port 202 is directly connected to the first end of the second heat exchange unit 10b. This facilitates the distribution of refrigerants of different pressures and flows into the four-way reversing valve and the second heat exchange unit.

[0071] Of course, referring to Figures 10 to 13 , in other embodiments, a single exhaust port may be provided. The refrigerant system further includes a diverter pipe 92 having two interconnected diverter outlets 921. The air inlet of the diverter pipe 92 is connected to the exhaust port. One diverter outlet 921 is connected to the D port of the four-way reversing valve 81, and the other diverter outlet 921 is connected to the first end of the second heat exchange portion 10b. This simplifies the structure of the refrigerant system and reduces its manufacturing and maintenance costs.

[0072] Referring to Figures 1 to 13, in some embodiments, the refrigerant system further includes a first throttling device 30, wherein a first end of the first throttling device 30 is connected to the second end of the first heat exchange portion 10a and the second end of the second heat exchange portion 10b, and a second end of the first throttling device 30 is connected to the first end of the second heat exchanger 40. Specifically, in a first mode, the refrigerant flowing out of the first heat exchange portion 10a and the refrigerant flowing out of the first heat exchange portion 10b merge and flow together into the first throttling device 30, then flow through the first throttling device 30 and the second heat exchanger 40 and return to the compressor 20, as shown in Figures 1, 6, or 10; in a second mode, the refrigerant flowing out of the second heat exchanger 40 flows into the first throttling device 30, and after being throttled by the first throttling device 30, merges with the refrigerant flowing out of the first heat exchange portion 10b, then flows together to the first heat exchange portion 10a, and finally returns to the compressor 20 through the return air port of the compressor 20, as shown in Figures 2, 7, or 11. In this way, the first throttling device 30 can throttle the refrigerant from the first heat exchange part 10a and the first heat exchange part 10b at the same time in the first mode, which is beneficial to improving the heat exchange efficiency of the refrigerant in the second heat exchanger 40.

[0073] Of course, in other embodiments, the first end of the first throttling device 30 may be connected to the second end of the first heat exchange portion 10a, and the second end of the first throttling device 30 may be connected to the first end of the second heat exchanger 40 and the second end of the first heat exchange portion 10b, that is, the second end of the first heat exchange portion 10b is directly connected to the first end of the second heat exchanger 40; or the first end of the first throttling device 30 may be connected to the second end of the first heat exchange portion 10b, and the second end of the first throttling device 30 may be connected to the first end of the second heat exchanger 40 and the second end of the first heat exchange portion 10a, that is, the second end of the first heat exchange portion 10a is directly connected to the first end of the second heat exchanger 40. Of course, the first throttling device 30 may also be omitted.

[0074] Referring to Figures 1 to 9, in an embodiment in which the exhaust port includes a first exhaust port 201 and a second exhaust port 202, the refrigerant pressure configurations of the first exhaust port 201 and the second exhaust port 202 are different, and the refrigerant system further includes a second throttling device 51, the first end of the second throttling device 51 being connected to the second end of the first heat exchange portion 10a and the second heat exchange portion 10b in the first mode, where the refrigerant pressure is greater, and the second end of the second throttling device 51 being connected to the first end of the first throttling device 30. In this way, in the first mode, the second throttling device 51 can pre-throttle the refrigerant flow path with a higher pressure to reduce its refrigerant pressure, which is conducive to the refrigerant in the refrigerant flow path being merged with the refrigerant in the other refrigerant flow path downstream. Of course, in other embodiments, the second throttling device 51 may not be provided, and only the first throttling device 30 may be provided.

[0075] Please refer to Figures 1 to 4. In some embodiments, the refrigerant pressure of the first exhaust port 201 is higher than the refrigerant pressure of the second exhaust port 202, which is called a medium-pressure normal operation scheme. At this time, the high-pressure refrigerant can enter the second heat exchanger in the second mode to improve the defrosting efficiency and effect. Please refer to Figures 6 to 9. In other embodiments, the refrigerant pressure of the first exhaust port 201 is lower than the refrigerant pressure of the second exhaust port 202, which is called a high-pressure normal operation scheme. At this time, the high-pressure refrigerant can enter the first heat exchanger in the second mode to ensure the heating efficiency and effect of the first heat exchanger. Of course, in other embodiments, the refrigerant pressure of the first exhaust port 201 can also be equal to the refrigerant pressure of the second exhaust port 202.

[0076] Referring to Figures 1 to 4 , in the embodiment of medium-pressure normal operation, the second end of the second heat exchange portion 10b is connected to the first end of the first throttling device 30. This simplifies the structure of the refrigerant system without affecting its performance. It is worth noting that, in the second mode, the second throttling device 51 can also perform a second throttling on the combined refrigerant, thereby improving the heat exchange efficiency of the refrigerant entering the first heat exchange portion.

[0077] Specifically, referring to Figures 1 and 3 , in the first mode, the refrigerant flowing out of the second end of the first heat exchange unit 10a first passes through the throttling effect of the second throttling device 51 to reduce its pressure, then merges with the refrigerant flowing out of the second end of the second heat exchange unit, and both flow into the first end of the first throttling device 30. Referring to Figures 2 and 4 , in the second mode, the refrigerant flowing out of the first end of the second heat exchanger 40 first passes through the throttling effect of the first throttling device 30 to reduce its pressure, then merges with the refrigerant flowing out of the second end of the second heat exchange unit, and both flow into the second end of the second throttling device 51.

[0078] It can be understood that in this embodiment, by arranging the second throttling device 51 between the second end of the first heat exchange part 10a and the first end of the first throttling device 30, the second throttling device 51 can throttle the refrigerant flow path with a higher pressure in both the first mode and the second mode. The structure is simple and easy to implement.

[0079] Please refer to Figures 6 to 9. In the embodiment of high-pressure normal operation, the refrigerant system further includes a fourth throttling device 52, and the second end of the first heat exchange part 10a is connected to the first end of the first throttling device 30 through the fourth throttling device 52. It can be understood that in the first mode, since the pressure of the refrigerant flowing out of the first heat exchange part 10a is lower than that of the refrigerant flowing out of the second heat exchange part 10a, the fourth throttling device 52 is controlled to be in a fully open state to reduce its throttling and pressure-reducing effect on the refrigerant, while the second throttling device 51 is in a throttling state (i.e., between fully open and fully closed) to perform normal throttling and pressure reduction on the refrigerant, so that the pressures of the refrigerants flowing out of the second throttling device 51 and the fourth throttling device 52 can be closer to facilitate their confluence. In the second mode, both the second throttling device 51 and the fourth throttling device 52 are in a throttling state to throttle and reduce the pressure of the refrigerant twice in succession. Of course, in other embodiments, the fourth throttling device may not be provided.

[0080] Referring to Figures 10 to 13, in an embodiment in which the exhaust port is configured as one, a second throttling device 51 is provided, that is, the first end of the second throttling device 51 is connected to the second end of the first heat exchange portion 10a, and the second end of the second throttling device 51 is connected to the first end of the first throttling device 30. It can be understood that since the refrigerant pressures flowing out of the two branch outlets 921 are the same, therefore, referring to Figure 10, in the first mode, the second throttling device 51 is controlled to be in a fully open state so that the pressures of the refrigerant flowing out of the second throttling device 51 and the second heat exchange portion 10b are closer to each other to facilitate their confluence. Referring to Figure 11, in the second mode, the second throttling device 51 is controlled to switch to a throttling state, at which time the second throttling device 51 can perform secondary throttling and pressure reduction on the refrigerant after confluence. Of course, in other embodiments in which the exhaust port is configured as one, the second throttling device may not be provided.

[0081] It will be appreciated that in an embodiment in which only one exhaust port is provided, by adjusting the opening of the second throttling device 51, the refrigerant flow rate out of the two diversion outlets 921 can also be adjusted, thereby adjusting the refrigerant flow rate flowing into the first heat exchange section 10a and the second heat exchange section 10b in the first mode. For example, when the second throttling device 51 is in a fully closed state, refrigerant does not flow into the first heat exchange section 10a, and the refrigerant flow rate flowing into the second heat exchange section 10b reaches its maximum value.

[0082] Referring to Figures 3, 4, 8, 9, 12, 13, and 21, in other embodiments, the refrigerant system further comprises an economizer 61, an air supply line 62, and a third throttling device 63. A third refrigerant flow path 611 and a fourth refrigerant flow path 612 for heat exchange are provided within the economizer 61. The first end of the third refrigerant flow path 611 is connected to the second end of the first heat exchange portion 10a and the second end of the second heat exchange portion 10b. The first end of the second heat exchanger 40 is connected to the second end of the third refrigerant flow path 611 and the first end of the fourth refrigerant flow path 612. The second end of the fourth refrigerant flow path 612 is connected to the air supply port 204 of the compressor 20 via the air supply line 62. Thus, by adding the economizer 61, the air supply line 62, and the third throttling device 63, the effect of increasing enthalpy by supplying air can be achieved, thereby improving the operating efficiency of the refrigerant system and reducing energy consumption.

[0083] 3 and 4 , in some embodiments, the first end of the second throttling device 51 is connected to the second end of the first heat exchange section 10a, and the second end of the second throttling device 51 is connected to the first end of the third refrigerant flow path 611. Specifically, in the first mode, the refrigerant flowing out of the second end of the first heat exchange section 10a first passes through the throttling effect of the second throttling device 51 and has its pressure reduced, then merges with the refrigerant flowing out of the second end of the second heat exchange section, and together they flow into the first end of the third refrigerant flow path 611 of the economizer 61. In the second mode, the refrigerant flowing out of the first end of the second heat exchanger 40 first passes through the throttling effect of the first throttling device 30 and has its pressure reduced, then flows through the third refrigerant flow path 611 and merges with the refrigerant flowing out of the second end of the second heat exchange section, and together they flow into the second end of the first heat exchange section 10a.

[0084] In some embodiments, the first heat exchange section 10a and the second heat exchange section 10b are positioned adjacent to each other. Thus, when the refrigerant system is in the second mode, the first heat exchange section 10a and the second heat exchange section 10b can first exchange heat with each other, thereby reducing the cooling effect of the first heat exchange section 10a, acting as an evaporator, on the surrounding air, thereby reducing indoor temperature fluctuations. Of course, in other embodiments, the first heat exchange section 10a and the second heat exchange section 10b can also be positioned away from each other.

[0085] Referring to Figures 2, 14, and 15, in some embodiments, the refrigerant system further includes an indoor fan 91, which is used to drive air from the first heat exchange section 10a to the second heat exchange section 10b. Thus, when the refrigerant system is in the second mode, the air first flows through the first heat exchange section 10a, which acts as the evaporator, to be cooled and dehumidified, and then flows through the second heat exchange section 10b, which acts as the condenser, to be heated, thereby providing dry, warm air to the indoor space. Of course, in other embodiments, the indoor fan may also be used to drive air from the second heat exchange section 10b to the first heat exchange section 10a.

[0086] Referring to Figures 1 to 14 , in some embodiments, the first heat exchange portion 10a and the second heat exchange portion 10b are integrated into a single first heat exchanger 10. This simplifies the structure of the refrigerant system and facilitates transportation and installation. Of course, referring to Figure 15 , in other embodiments, the first heat exchange portion 10a and the second heat exchange portion 10b may be configured as two independent first heat exchangers 10.

[0087] Specifically, the first heat exchanger 10 can have various structural forms. For example, referring to Figures 14 or 15 , in an embodiment equipped with an indoor fan, the first heat exchanger 10 is provided with only a refrigerant flow path. That is, both the first heat exchange portion 10a and the second heat exchange portion 10b are provided with refrigerant flow paths, and the indoor fan drives air through the outer surfaces of the refrigerant flow paths to perform heat exchange. In this embodiment, the first heat exchanger 10 can be a fin-and-tube heat exchanger, a coil heat exchanger, or a microchannel flat tube heat exchanger, etc., and this application does not impose specific limitations.

[0088] Of course, the first heat exchanger 10 can also have other structural forms. For example, referring to Figures 16 to 20, in other embodiments, the first heat exchanger 10 is provided with a parallel refrigerant flow path and a water path that exchange heat with each other. That is, the first heat exchange part 10a and the second heat exchange part 10b are both provided with a parallel refrigerant flow path and a water path that exchange heat with each other. In this way, the water in the water path of the first heat exchanger 10 first exchanges heat with the refrigerant, then flows into the heating water pipe in the indoor space and exchanges heat with the indoor air to achieve temperature regulation of the indoor air. Of course, the water after heat exchange with the refrigerant can also be used as domestic hot water. In this case, the refrigerant system is a heat pump system and realizes the function of a heat pump water heater.

[0089] It can be understood that regardless of whether a single four-way reversing valve or other forms of control device 80 is used, the refrigerant system of the present application can realize the defrosting of the second heat exchanger 40 without stopping the compressor 20, and can reduce the water temperature fluctuation in the water circuit, thereby reducing the water temperature fluctuation of domestic hot water or heating hot water, and improving the thermal comfort of the indoor space and user experience.

[0090] In the embodiment where the first heat exchanger 10 is provided with a parallel refrigerant flow path and a water path for heat exchange, the first heat exchanger 10 is configured as a plate heat exchanger. Of course, in other embodiments, the first heat exchanger may also be configured as a fin-tube heat exchanger, a coil heat exchanger, or a microchannel flat tube heat exchanger.

[0091] Please refer to Figures 16 to 20, wherein Figures 16 and 17 show structural schematic diagrams of two embodiments of the plate heat exchanger of the present application, the solid arrows in the figures indicate the flow direction of water, and the hollow arrows indicate the flow direction of the refrigerant; Figures 18 to 20 show water flow schematic diagrams of three embodiments of the plate heat exchanger of the present application, and the embodiment shown in Figure 18 corresponds to the embodiment shown in Figure 16, the solid arrows in the figure indicate the flow direction of water, and the dotted arrows indicate the flow direction of the refrigerant, the upper horizontal waterway in the figure corresponds to the first flow hole in the upper right corner of the plate shown in Figure 16, and the lower horizontal waterway corresponds to the first flow hole in the lower right corner of the plate shown in Figure 16.

[0092] Specifically, please refer to Figures 16 to 20. In some embodiments, the refrigerant flow path includes a first refrigerant flow path 101 and a second refrigerant flow path 102. The water path includes a first water path 103 corresponding to the first refrigerant flow path 101, and a second water path 104 corresponding to the second refrigerant flow path 102. The water path is provided with a water inlet 105, a first water outlet 106 corresponding to the first water path 103, and a second water outlet 107 corresponding to the second water path 104. The first refrigerant flow path 101 and the second refrigerant flow path 102 are both provided with a liquid inlet 108 and a liquid outlet 109. That is, the plate heat exchanger is configured as a structure with independent dual refrigerant flow paths and sharing the same water path. Specifically, the first refrigerant flow path 101 corresponds to the refrigerant flow path on the first heat exchange part 10a, and the second refrigerant flow path 102 corresponds to the refrigerant flow path on the second heat exchange part 10b; the first water path 103 corresponds to the water path on the first heat exchange part 10a, and the second water path 104 corresponds to the water path on the second heat exchange part 10b.

[0093] In this embodiment, by simultaneously providing a first water outlet 106 and a second water outlet 107 on a single plate heat exchanger 10 system, the water in the first water path 103 and the second water path 104 can be output from the first water outlet 106 and the second water outlet 107 respectively after undergoing different degrees of heat exchange, thereby providing hot water at two different water temperatures to simultaneously meet different heating needs. Specifically, the hot water output from the first water outlet 106 and the second water outlet 107 can be used as domestic hot water, while the hot water at a lower temperature can be used as heating water. In this way, a single plate heat exchanger 10 can simultaneously supply water at different outlet temperatures, thereby reducing the initial investment cost and subsequent maintenance costs of the equipment, that is, reducing the cost of using the refrigerant system.

[0094] It is understandable that in a scheme where a multi-connected heating system is used to meet the needs of hot water supply at two water temperatures, if heating hot water is prioritized, then domestic hot water will require additional electric auxiliary heating due to the outlet water temperature not meeting the standard, resulting in a large amount of electricity consumption; if domestic hot water is prioritized, that is, the outlet water temperature is higher, then the heating facilities will need to be mixed with cold water to achieve the required relatively low-temperature hot water, which also consumes a lot of energy. The plate heat exchanger 10 of the present application has a single-inlet and dual-outlet water system, and can simultaneously provide two hot waters of different water temperatures to the outside after the water in the first water channel 103 and the second water channel 104 undergoes different degrees of heat exchange, thereby simultaneously meeting the needs of domestic hot water and heating hot water, thereby reducing the energy consumption of the refrigerant system.

[0095] Please refer to Figure 16 or Figure 17. In some embodiments, the plate heat exchanger 10 includes a plurality of plates, and the plurality of plates include a plurality of water channel plates 13 and refrigerant flow channel plates 14 that are alternately distributed. The plates have two first flow holes 15 for water circulation and two second flow holes 16 for refrigerant circulation. The inner cavity of the water channel plate 13 is connected to the first flow holes 15 and separated from the second flow holes 16. The inner cavity of the refrigerant flow channel plate 14 is connected to the second flow holes 16 and separated from the first flow holes 15.

[0096] Furthermore, the two second flow holes 16 of the outermost plate of the first end 10c are respectively connected to a group of liquid inlets 108 and liquid outlets 109, and the two second flow holes of the outermost plate of the second end 10d are respectively connected to another group of liquid inlets 108 and liquid outlets 109.

[0097] Specifically, please refer to Figure 16. The two first circulation holes 15 and the two second circulation holes 16 are respectively arranged at the four corners of the plate. Regardless of the water channel plate 13 or the refrigerant flow channel plate 14, the two first circulation holes 15 on the left are used to transport refrigerant, and the two second circulation holes 16 on the right are used to transport water; the inner cavity of the refrigerant flow channel plate 14 is only connected to the two second circulation holes 16 on the left, and the inner cavity of the water channel plate 13 is only connected to the two first circulation holes 15 on the right.

[0098] It is understood that there are various ways to achieve different levels of heat exchange. For example, referring to Figures 16, 18, and 19, in some embodiments, the water inlet 105 is connected to the first water path 103, and the first water path 103 and the second water path 104 are connected in series, so that the outlet water temperatures of the first water outlet 106 and the second water outlet 107 are different. In this embodiment, a portion of the water flowing into the plate heat exchanger 10 through the water inlet 105 flows through the first water path 103 and then directly flows out of the first water outlet 106, while the other portion continues to flow through the second water path 104 and then flows out of the second water outlet 107. In this way, the hot water flowing out of the second water outlet 107 has a higher water temperature after undergoing two heat exchanges. It is understood that at this time, the refrigerant temperatures in the first refrigerant flow path 101 and the second refrigerant flow path 102 can be set to be the same or different.

[0099] In one embodiment, referring to FIG. 16 , the plate heat exchanger 10 has a first end 10c and a second end 10d opposite each other. The first end 10c is disposed in the first heat exchange portion 10a, and the second end 10d is disposed in the second heat exchange portion 10b. A first flow hole 15 of the outermost plate of the first end 10c is connected to the water inlet 105, and a first flow hole 15 of the outermost plate of the second end 10d corresponding to the water inlet 105 is connected to the second water outlet 107. A partition 11 is provided in the first flow hole 15 of the middle plate corresponding to the water inlet 105 to connect the first water path 103 and the second water path 104 in series.

[0100] Specifically, please refer to Figure 16. The first flow hole 15 on the upper right of the refrigerant flow path plate 14 at the outermost side of the first end 10c is connected to the water inlet 105, and the first flow hole 15 on the lower right of the refrigerant flow path plate 14 is provided with a partition 11 to block water from flowing through the first flow hole 15. The two second flow holes 16 on the upper left and lower left of the refrigerant flow path plate 14 are respectively connected to the external refrigerant pipe to form a first independent refrigerant circuit; the first flow hole 15 on the upper right of the refrigerant flow path plate 14 at the outermost side of the second end 10d is connected to the second water outlet 107. The refrigerant flow plate 14 is connected to the second refrigerant pipe, and the second flow holes 16 at the upper left and lower left of the refrigerant flow plate 14 are connected to the external refrigerant pipe to form a second independent refrigerant circuit. The first flow hole 15 at the upper right of the refrigerant flow plate 14 in the middle is equipped with a partition 11 to block water from flowing through the first flow hole 15. In this way, the water in the first heat exchange part 10a cannot flow into the second heat exchange part 10b through the first flow hole 15 and can only flow into the second heat exchange part 10b through the first flow hole 15 at the lower right of the refrigerant flow plate 14, thereby achieving the series connection of the first water path and the second water path. In this way, the hot water flowing out of the second water outlet 107 has undergone two heat exchanges in the first heat exchange part and the second heat exchange part, and has a higher water temperature.

[0101] It can be understood that the outermost plate located at the first end 10c and the outermost plate located at the first end 10c can also be a water channel plate, and is not necessarily limited to the refrigerant flow channel plate of the embodiment shown in Figure 16. This application does not make specific limitations on this.

[0102] The second water outlet 107 may be arranged in various positions. For example, referring to Figures 16 and 18, in one embodiment, another first flow hole 15 of the plate located at the outermost side of the first end 10c is provided with a partition 11, and another first flow hole 15 of the plate located at the outermost side of the second end 10d is connected to the first water outlet 106. Of course, in another embodiment, another first flow hole 15 of the plate located at the outermost side of the first end 10c may be connected to the first water outlet 106, and another first flow hole 15 of the plate located at the outermost side of the second end 10d may be provided with a partition 11.

[0103] Specifically, referring to Figures 16 and 18 , in one embodiment, a partition 11 is provided at the lower right first flow hole 15 of the refrigerant flow plate 14 located at the outermost portion of the first end portion 10c to prevent water from flowing out of the plate heat exchanger through the first flow hole 15. The lower right first flow hole 15 of the refrigerant flow plate 14 located at the outermost portion of the second end portion 10d is connected to the first water outlet 106. In this case, the first water outlet 106 and the second water outlet 107 are arranged in the same direction, which facilitates the centralized layout of the water outlet pipelines.

[0104] Please refer to Figure 19. In another embodiment, the first water outlet 106 and the second water outlet 107 are arranged in opposite directions. Specifically, the first flow hole 15 at the lower right corner of the refrigerant flow plate 14 located at the outermost end 10c is connected to the first water outlet 106, and the first flow hole 15 at the lower right corner of the refrigerant flow plate 14 located at the outermost end 10d is provided with a partition 11 to block water from flowing out of the plate heat exchanger through the first flow hole 15.

[0105] It can be understood that the partition 11 can be directly formed on the plate, that is, the partition 11 is directly integrally formed when the plate is manufactured. In this case, there is no first flow hole 15 in the area corresponding to the partition 11 after the plate is manufactured; the partition 11 can also be formed separately from the plate and then assembled into one. In this case, the manufactured plate has four through holes, and the partition 11 is assembled and fixed in the first flow hole 15 of the plate by bonding, welding, etc.

[0106] Referring to Figure 16 , in one embodiment, the baffle 11 for changing the refrigerant flow direction (referred to as the refrigerant-side baffle 11 ) and the baffle 11 for changing the water flow direction (referred to as the water-side baffle 11 ) are located on different plates. Specifically, in this embodiment, the refrigerant-side baffle 11 is located on an adjacent plate located in front of the water-side baffle 11 . Of course, in other embodiments, the refrigerant-side baffle 11 may also be located on an adjacent plate located behind the water-side baffle 11 .

[0107] Please refer to Figure 17. In another embodiment, the refrigerant side baffle 11 and the water side baffle 11 can also be provided on the same plate. Specifically, the fourth plate in the direction from front to back is provided with both the refrigerant side baffle 11 and the water side baffle 11. In this case, the water side baffle 11 is provided as a half baffle, that is, the water side baffle 11 only blocks the rear side of the first flow hole 15 in the upper right corner of the plate, but the first flow hole 15 is still connected to the inner cavity of the plate. In this case, water cannot flow through the first flow hole 15 but can turn and flow into the inner cavity of the plate. Since a half baffle refers to a single side of the first flow hole 15 being blocked, correspondingly, a full baffle refers to both the front and rear sides of the first flow hole 15 being blocked. It can be understood that at this time, the refrigerant side baffle 11 can be either a full baffle or a half baffle, and the refrigerant will not flow into the plate.

[0108] Of course, in other embodiments, the fifth plate in the direction from front to back may be provided with both a refrigerant-side baffle 11 and a water-side baffle 11. In this case, the refrigerant-side baffle 11 is provided as a half baffle, while the water-side baffle 11 may be either a full baffle or a half baffle. Those skilled in the art may adjust the placement of the baffles 11 as needed.

[0109] Of course, other methods can also be used to achieve different degrees of heat exchange. For example, referring to Figure 20, in another embodiment, the water inlet 105 is connected to both the first water channel 103 and the second water channel 104, and the pressure of the refrigerant flowing into the first refrigerant channel 101 and the second refrigerant channel 102 is configured to be different, so that the outlet water temperatures of the first water outlet 106 and the second water outlet 107 are different. In one embodiment, one water-side baffle of this embodiment is provided on the outermost refrigerant channel plate at the second end portion 10d, and another water-side baffle is provided on the middle refrigerant channel plate, so that the water flowing into the plate heat exchanger 10 through the water inlet 105 is divided into two streams, which flow through the first water channel 103 and the second water channel 104 respectively, and respectively exchange heat with the refrigerant in the first refrigerant channel 101 and the second refrigerant channel 102, and then the two hot water streams flow out of the plate heat exchanger separately. By setting the refrigerant temperatures in the two refrigerant flow paths to be different, different heat exchange levels can be achieved in the first water path 103 and the second water path 104. That is, the first water path 103 and the second water path 104 are arranged in parallel.

[0110] It can be understood that the use of a single compressor 20 to output multiple streams of refrigerant with different pressures is based on the idea of ​​energy cascade utilization. Therefore, this application does not specifically limit the number of exhaust ports, refrigerant flow paths and water paths of the compressor 20. That is, when a large-displacement compressor 20 with three or more exhaust ports is used, the plate heat exchanger 10 can be simultaneously provided with a corresponding number of refrigerant flow paths and water paths, thereby giving full play to the effect of energy cascade utilization.

[0111] Specifically, in an embodiment where the refrigerant pressure at the first exhaust port 201 is higher than the refrigerant pressure at the second exhaust port 202, the first exhaust port 201 is connected to the second refrigerant flow path 102, and the second exhaust port 202 is connected to the first refrigerant flow path 101. That is, in the first mode, the high-pressure exhaust gas from the compressor 20 flows into the second refrigerant flow path 102, while the medium-pressure exhaust gas flows into the first refrigerant flow path 101. As a result, the water flowing out of the second water path 104 is at a higher temperature and can be used as domestic hot water, while the water flowing out of the first water path 103 is at a lower temperature and can be used as heating water.

[0112] Of course, in other embodiments, the refrigerant temperatures of the first refrigerant flow path 101 and the second refrigerant flow path 102 may be configured to be the same, while the effective heat exchange areas of the first water path 103 and the second water path 104 may be configured to be different. For example, in an embodiment where the water inlet 105 is connected to both the first water path 103 and the second water path 104, the heat exchange path between the first refrigerant flow path 101 and the first water path 103 is longer, or the total heat exchange area between the two is larger, thereby causing the water temperature at the first water outlet 106 to be higher.

[0113] 16 to 20 , it can be understood that in the embodiment of the present application, regardless of the flow direction of water in the first water channel 103 and the second water channel 104 , the flow direction of the refrigerant is configured to be opposite thereto, thereby improving the heat exchange efficiency between water and refrigerant.

[0114] Please refer to Figure 21. In some embodiments, a flow valve 12 is provided on the first water outlet 106 and / or the second water outlet 107 to adjust the water flow rate of the first water outlet 106 and the second water outlet 107. In this way, by controlling the flow valve 12, the water flow rate can be adjusted, and the flow rate and water temperature of the corresponding water circuit can be adjusted according to the user's load requirements, that is, variable load regulation is achieved, thereby improving the ease of use and flexibility of the refrigerant system. It can be understood that if the flow valve 12 is completely closed, the water circuit of the plate heat exchanger 10 changes from a single-inlet and dual-outlet system to a single-inlet and single-outlet system. Of course, in other embodiments, solenoid valves can be provided at both the first water outlet 106 and the second water outlet 107, or the flow valve 12 is not provided.

[0115] The water temperature at the first water outlet 106 is lower than that at the second water outlet 107, and the flow valve 12 is provided at the first water outlet 106. Thus, placing the flow valve 12 at the first water outlet 106, where the water temperature is lower, completely closes the first water outlet 106, thereby satisfying the user's need to use only domestic hot water. Of course, in other embodiments, the flow valve 12 may also be provided at the second water outlet 107, or both the first water outlet 106 and the second water outlet 107 may be provided with a flow valve 12.

[0116] Referring to Figure 21 , in one embodiment, the refrigerant system further includes a gas-liquid separator 70 , which connects the second end of the second heat exchanger 40 to the return air port of the compressor 20 . This prevents refrigerant liquid hammer. Of course, in other embodiments, the gas-liquid separator 70 may not be provided.

[0117] The above description is merely an optional embodiment of the present application and does not limit the patent scope of the present application. All equivalent structural transformations made using the contents of the present application specification and drawings under the inventive concept of the present application, or direct / indirect application in other related technical fields are included in the patent protection scope of the present application.

Claims

1. A refrigerant system, wherein: The refrigerant system comprises: a compressor having an exhaust port; a first heat exchanger and a second heat exchanger connected to the compressor, wherein the first heat exchanger includes a first heat exchange portion and a second heat exchange portion, wherein the first heat exchange portion and the second heat exchange portion are provided with a refrigerant flow path and a water path for heat exchange with each other; and A control device, wherein the control device is capable of controlling the refrigerant system to switch between a first mode and a second mode, wherein in the first mode, a refrigerant circuit is formed between the compressor and the first heat exchange part and the second heat exchanger, and a refrigerant circuit is formed between the compressor and the second heat exchange part and the second heat exchanger; and in the second mode, a refrigerant circuit is formed between the compressor and the second heat exchanger and the first heat exchange part, and a refrigerant circuit is formed between the compressor and the second heat exchange part and the first heat exchange part.

2. The refrigerant system according to claim 1, wherein: The compressor also has a return air port, and the control device includes a four-way reversing valve. The first end of the second heat exchange part is connected to the exhaust port, the first interface of the four-way reversing valve is connected to the first end of the first heat exchange part, the second interface of the four-way reversing valve is connected to the second end of the second heat exchanger, the third interface of the four-way reversing valve is connected to the exhaust port, the fourth interface of the four-way reversing valve is connected to the return air port, and the first end of the second heat exchanger is connected to the second end of the first heat exchange part and the second end of the second heat exchange part.

3. The refrigerant system according to claim 2, wherein: The refrigerant system further includes a first throttling device, a first end of the first throttling device is connected to the second end of the first heat exchange part and the second end of the second heat exchange part, and a second end of the first throttling device is connected to the first end of the second heat exchanger.

4. The refrigerant system according to claim 3, wherein: The exhaust port includes a first exhaust port and a second exhaust port, the first exhaust port is connected to the third interface of the four-way reversing valve, and the second exhaust port is connected to the first end of the second heat exchange part.

5. The refrigerant system according to claim 4, wherein: The refrigerant system also includes a second throttling device, a first end of which is connected to the second end of the first heat exchange part and the second heat exchange part where the refrigerant pressure is larger in the first mode, and a second end of the second throttling device is connected to the first end of the first throttling device.

6. The refrigerant system according to claim 5, wherein: The refrigerant pressure of the first exhaust port is higher than the refrigerant pressure of the second exhaust port, and the second end of the second heat exchange part is connected to the first end of the first throttling device; or The refrigerant pressure of the first exhaust port is lower than the refrigerant pressure of the second exhaust port. The refrigerant system also includes a fourth throttling device, and the second end of the first heat exchange part is connected to the first end of the first throttling device through the fourth throttling device.

7. The refrigerant system according to claim 3, wherein: The exhaust port is configured as one, and the refrigerant system also includes a diverter pipeline, which has two connected diverter outlets. The air inlet of the diverter pipeline is connected to the exhaust port, one of the diverter outlets is connected to the third interface of the four-way reversing valve, and the other diverter outlet is connected to the first end of the second heat exchange part.

8. The refrigerant system according to claim 7, wherein: The refrigerant system further includes a second throttling device, a first end of the second throttling device is connected to the second end of the first heat exchange part, and a second end of the second throttling device is connected to the first end of the first throttling device.

9. The refrigerant system according to claim 5 or 8, wherein: The refrigerant system also includes an economizer, an air supply pipeline and a third throttling device. The economizer is provided with a third refrigerant flow path and a fourth refrigerant flow path for heat exchange. The first end of the third refrigerant flow path is connected to the second end of the first heat exchange part and the second end of the second heat exchange part. The first end of the second heat exchanger is connected to the second end of the third refrigerant flow path and the first end of the fourth refrigerant flow path. The second end of the fourth refrigerant flow path is connected to the air supply port of the compressor through the air supply pipeline.

10. The refrigerant system according to claim 9, wherein: The first end of the second throttling device is connected to the second end of the first heat exchange part, and the second end of the second throttling device is connected to the first end of the third refrigerant flow path.

11. The refrigerant system according to any one of claims 1 to 8, wherein: The first heat exchange portion and the second heat exchange portion are arranged adjacent to each other.

12. The refrigerant system according to claim 11, wherein: The first heat exchange part and the second heat exchange part are integrated into a same first heat exchanger.

13. The refrigerant system of claim 12, wherein: The first heat exchanger is configured as a plate heat exchanger and is provided with a refrigerant flow path and a water path for heat exchange. The refrigerant flow path includes a first refrigerant flow path and a second refrigerant flow path. The water path includes a first water path corresponding to the first refrigerant flow path and a second water path corresponding to the second refrigerant flow path. The water path is provided with a water inlet, a first water outlet corresponding to the first water path, and a second water outlet corresponding to the second water path.

14. The refrigerant system of claim 13, wherein: The water inlet is connected to the first water path and the second water path, and the pressures of the refrigerants flowing through the first refrigerant flow path and the second refrigerant flow path are configured to be different, so that the outlet water temperatures of the first water outlet and the second water outlet are different; or The water inlet is communicated with the first water channel, and the first water channel and the second water channel are connected in series, so that the outlet water temperatures of the first water outlet and the second water outlet are different.

15. The refrigerant system of claim 14, wherein: The first water outlet and / or the second water outlet is provided with a flow valve to adjust the water flow rate of the first water outlet and the second water outlet.

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