Outdoor main machine and air source heat pump system

Abstract

The utility model discloses an outdoor main machine and an air source heat pump system. The outdoor main machine comprises a shell, an outdoor side heat exchange module, a compressor, a high-pressure gas-liquid separator, a low-pressure gas-liquid separator and an electric control module. A first cavity and a second cavity are formed in the shell, and the second cavity is located on the horizontal side of the first cavity. And the outdoor side heat exchange module is arranged in the first cavity. And the compressor, the high-pressure gas-liquid separator and the low-pressure gas-liquid separator are arranged in the second cavity. And at least part of the electric control module is arranged in the second cavity. In the vertical direction, the high-pressure gas-liquid separator is located between the electric control module and the compressor. The internal space of the host is fully utilized, so that the space layout is more reasonable, the miniaturization of the product is realized, and meanwhile, the pipeline connection among all parts is also facilitated.

Description

TECHNICAL FIELD

[0001] The utility model relates to outdoor mainframe technical field especially relates to a kind of outdoor mainframe and air source heat pump system. BACKGROUND

[0002] The heat pump mainframe of relevant technology is generally provided with low-pressure gas-liquid separator, but rarely high-pressure gas-liquid separator, because it cannot well solve the problem of limited internal space and complex pipeline setting of mainframe. INVENTION CONTENTS

[0003] The technical problem to be solved by the utility model is that, at least one defect of relevant technology mentioned in the above background technology: the internal space of heat pump mainframe is limited, rarely high-pressure gas-liquid separator is provided, a kind of outdoor mainframe and air source heat pump system are provided.

[0004] The technical scheme that the utility model solves its technical problem is: a kind of outdoor mainframe is structured, comprising:

[0005] Shell, the first cavity and the second cavity are formed in the shell, and the second cavity is located on the horizontal side of the first cavity;

[0006] Outdoor side heat exchange module, the outdoor side heat exchange module is arranged in the first cavity;

[0007] Compressor, high-pressure gas-liquid separator and low-pressure gas-liquid separator, the compressor, the high-pressure gas-liquid separator and the low-pressure gas-liquid separator are arranged in the second cavity;And,

[0008] Electric control module, the electric control module is at least partially arranged in the second cavity;And in vertical direction, the high-pressure gas-liquid separator is located between the electric control module and the compressor.

[0009] Some embodiments, the outdoor mainframe further comprises:

[0010] Partition, the partition is arranged in the shell, and the partition divides the internal space surrounded by the shell into adjacent first cavity and second cavity.

[0011] Some embodiments, the electric control module is located above the partition, a part of the electric control module is arranged in the second cavity, another part of the electric control module is arranged in the first cavity, and the electric control module is provided with heat dissipation channel that communicates the first cavity and the second cavity on the electric control module.

[0012] Some embodiments, the high-pressure gas-liquid separator is arranged on the partition.

[0013] Some embodiments, the compressor and the low-pressure gas-liquid separator are arranged at the bottom of the second cavity.

[0014] In some embodiments, the outdoor main machine further comprises:

[0015] a first reversing valve and an economizer, which are arranged in the second cavity, and a first switch valve and a second switch valve, which are arranged corresponding to the second cavity; one end of the first switch valve is connected with the first reversing valve; one end of the second switch valve is connected with the economizer;

[0016] a third switch valve and a fourth switch valve, which are arranged corresponding to the second cavity; one end of the third switch valve is connected with the outlet of the compressor; one end of the fourth switch valve is connected with the first refrigerant inlet of the high-pressure gas-liquid separator.

[0017] In some embodiments, the economizer is arranged on the partition plate.

[0018] In some embodiments, the outdoor main machine further comprises:

[0019] a fixing plate, which is arranged in the second cavity and connected with the partition plate and the shell, and the first switch valve and the second switch valve are arranged on the fixing plate and located in the second cavity;

[0020] the third switch valve and the fourth switch valve are arranged on the shell and located outside the second cavity.

[0021] In some embodiments, the first reversing valve is located at the middle of the vertical direction of the second cavity, and the first switch valve and the second switch valve are located below the first reversing valve; and / or, the third switch valve and the fourth switch valve are located above the first reversing valve.

[0022] The utility model further constructs an air source heat pump system, comprising any one of the outdoor main machine described above.

[0023] By implementing the utility model, the following beneficial effects are achieved:

[0024] The outdoor main machine has a first cavity and a second cavity inside, an outdoor side heat exchange module is arranged in the first cavity, a compressor, a high-pressure gas-liquid separator and a low-pressure gas-liquid separator are arranged in the second cavity, and an electric control module is at least partially arranged in the second cavity, and in the vertical direction, the high-pressure gas-liquid separator is located between the electric control module and the compressor, so that the space inside the main machine is fully utilized, the space layout is more reasonable, the product is miniaturized, and the pipeline connection between the various components is facilitated. BRIEF DESCRIPTION OF DRAWINGS

[0025] The utility model will be further described below in combination with the drawings and embodiments, wherein:

[0026] Figure 1 The overall structure diagram of one embodiment of the outdoor main machine of the utility model is shown;

[0027] Figure 2 The internal structure diagram of one embodiment of the outdoor main machine of the utility model is shown;

[0028] Figure 3 The first internal structure diagram of the second cavity of one embodiment of the outdoor main machine of the utility model is shown;

[0029] Figure 4 The second internal structure diagram of the second cavity of one embodiment of the outdoor main machine of the utility model is shown;

[0030] Figure 5 The air inlet schematic diagram of the electric control module of one embodiment of the outdoor main machine of the utility model is shown;

[0031] Figure 6 The air outlet schematic diagram of the electric control module of one embodiment of the outdoor main machine of the utility model is shown;

[0032] Figure 7 It is the schematic diagram of the air source heat pump system of the utility model;

[0033] Figure 8 It is the refrigerant flow direction schematic diagram of the air source heat pump system of the utility model in the refrigeration through the total heat recovery mode preparing hot water at the same time;

[0034] Figure 9 It is the first refrigerant flow direction schematic diagram of the air source heat pump system of the utility model in the refrigeration through the waste heat recovery mode preparing hot water at the same time;

[0035] Figure 10 It is the second refrigerant flow direction schematic diagram of the air source heat pump system of the utility model in the refrigeration through the waste heat recovery mode preparing hot water at the same time;

[0036] Figure 11 It is the first refrigerant flow direction schematic diagram of the air source heat pump system of the utility model in the heating preparing hot water at the same time;

[0037] Figure 12 It is the second refrigerant flow direction schematic diagram of the air source heat pump system of the utility model in the heating preparing hot water at the same time;

[0038] Figure 13 It is the refrigerant flow direction schematic diagram of the air source heat pump system of the utility model in the pure preparation hot water;

[0039] Figure 14is the refrigerant flow direction schematic view of the air source heat pump system in the refrigeration of the utility model;

[0040] Figure 15 is the refrigerant flow direction schematic view of the air source heat pump system in the heating of the utility model. DETAILED DESCRIPTION

[0041] In order to have a clearer understanding of the technical features, objects and effects of the utility model, the specific embodiments of the utility model will be described in detail with reference to the drawings.

[0042] It should be noted that the embodiments in the utility model and the features in the embodiments can be combined with each other without conflict.

[0043] In the description of the utility model, it should be understood that the orientation or position relationship indicated by the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the utility model and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements indicated must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the utility model. In addition, the terms "first", "second" and the like are only for the purpose of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features limited by "first", "second" and the like can explicitly or implicitly include one or more features. In the description of the utility model, unless otherwise specified, the meaning of "a plurality of" is two or more.

[0044] In the description of the utility model, it should be noted that, unless otherwise specified and limited, the terms "mounting", "connection", "connection", "set in", "located" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrally connected, it can be mechanically connected, or it can be chemically connected, it can be directly connected, or it can be indirectly connected through an intermediate medium, it can be the communication between two elements. For ordinary skilled in the art, the specific meaning of the above terms in the utility model can be understood according to the specific circumstances.

[0045] It can be understood that the "set in" described below is detachable connection or fixed connection, and the detachable connection can be screw locking, clamping and the like, and the fixed connection can be welding or integral molding and the like. And the connection between the ports, between the ports and the components or between the components is only the direct connection or indirect connection of the physical structure through the pipeline, and the communication relationship and the refrigerant flow relationship are not uniquely limited.

[0046] As Figure 1、 Figure 2 and Figure 3 As shown in

[0047] As shown in Figure 2 , the shell 11 has a first cavity 111 and a second cavity 112 inside, and the second cavity 112 is located on one side of the first cavity 111. The outdoor heat exchange module is arranged in the first cavity 111. The compressor 12, the high-pressure gas-liquid separator 13 and the low-pressure gas-liquid separator 14 are arranged in the second cavity 112. The electric control module 15 is at least partially arranged in the second cavity 112, and it can be understood that at least part of it can be part or all. In the vertical direction, the high-pressure gas-liquid separator 13 is located between the electric control module 15 and the compressor 12.

[0048] It should be noted that the height direction H of the shell 11 shown in Figure 1 is the vertical direction, and the length direction L of the shell 11 is the horizontal direction.

[0049] This embodiment makes full use of the space inside the host, makes the space layout more reasonable, realizes the miniaturization of the product, and also facilitates the pipeline connection between the various components.

[0050] Some embodiments, as shown in Figure 2 , the outdoor host also includes a partition 16, the partition 16 is arranged inside the shell 11 along the vertical direction, the partition 16 divides the internal space surrounded by the shell 11 into adjacent first cavity 111 and second cavity 112, such as the first cavity 111 and the second cavity 112 are cuboids, and the volume of the first cavity 111 is greater than the volume of the second cavity 112.

[0051] Some embodiments, the compressor 12 is used to compress refrigerant, the high-pressure gas-liquid separator 13 and the low-pressure gas-liquid separator 14 are used to realize gas-liquid separation of refrigerant, as shown in Figure 3 , the compressor 12, the high-pressure gas-liquid separator 13 and the low-pressure gas-liquid separator 14 are all tanks extending along the vertical direction, wherein the compressor 12 and the low-pressure gas-liquid separator 14 are arranged at the bottom of the second cavity 112, and the high-pressure gas-liquid separator 13 is arranged on the partition 16.

[0052] As shown in Figure 7As shown, the high-pressure gas-liquid separator 13 comprises a first refrigerant inlet 131, a first refrigerant outlet 132 and a second refrigerant outlet 133. The first refrigerant inlet 131 is configured to be connected to the third refrigerant outlet 402 of the external hot water module to input the heat-exchanged refrigerant. The first refrigerant outlet 132 is configured to output the gaseous refrigerant after gas-liquid separation. The second refrigerant outlet 133 is configured to output the liquid refrigerant after gas-liquid separation.

[0053] In some embodiments, as shown in Figure 2 As shown, the outdoor heat exchange module comprises an outdoor heat exchanger 17 and at least one fan 18. It is understood that the number of the fan 18 can be one, two, three or any number. As shown in Figure 7 As shown, the outdoor heat exchanger 17 comprises a first refrigerant port 171 and a second refrigerant port 172. The first refrigerant port 171 is in communication with the second refrigerant port 172. The first refrigerant port 171 is connected to the outlet of the compressor 12, the first refrigerant outlet 132 of the high-pressure gas-liquid separator 13 and the inlet of the low-pressure gas-liquid separator 14. The second refrigerant port 172 is configured to be connected to the external indoor unit 52 and the second refrigerant outlet 133 of the high-pressure gas-liquid separator 13.

[0054] When the heat pump system is running, the fan 18 is started and drives the external air to exchange heat with the refrigerant in the outdoor heat exchanger 17. Specifically, two fans 18 are arranged in the vertical direction in the first cavity 111. The outdoor heat exchanger 17 is a finned heat exchanger and is arranged around the vertical direction on the two sides opposite and adjacent to the partition plate 16 in the first cavity 111. The outdoor heat exchanger 17 is in the shape of “L”.

[0055] In some embodiments, as shown in Figure 2 As shown, the electric control module 15 is configured to control the electric control components in the outdoor main unit, such as the compressor 12, the outdoor heat exchange module, etc. The electric control module 15 is located above the partition plate 16. A part of the electric control module 15 is arranged in the second cavity 112 and the other part of the electric control module 15 is arranged in the first cavity 111. The electric control module 15 is provided with a heat dissipation channel which communicates the first cavity 111 and the second cavity 112, as shown in Figure 5 and Figure 6As shown, the heat dissipation passage includes an air inlet 151 located in the second cavity 112 and an air outlet 152 located in the first cavity 111. In some other embodiments, the electric control module 15 can be located in the second cavity 112 as a whole, and the electric control module 15 is provided with a heat dissipation passage which communicates the first cavity 111 and the second cavity 112, and the heat dissipation passage includes an air inlet located in the second cavity 112 and an air outlet formed on the partition plate 16.

[0056] When the compressor 12 and other components work in the second cavity 112, heat will be generated and gathered at the electric control module 15 at the top. Therefore, when the fan 18 is started, the air flow between the first cavity 111 and the outside can be realized, and the first cavity 111 forms a negative pressure, i.e. has a suction effect, so that the air flow of the second cavity 112 enters from the air inlet, flows through the inside of the electric control module 15, takes away the heat of the second cavity 112, and then the hot air enters the first cavity 111 for heat dissipation. This scheme can avoid the heat of the second cavity 112 from gathering at the electric control module 15, realize effective and rapid heat dissipation at the electric control module 15, and has good heat dissipation effect, so that the performance of the electric control module 15 can be avoided from being affected by the high temperature.

[0057] In some embodiments, as shown in Figure 3 The outdoor main unit further includes a first reversing valve 19, an economizer 20, a first on-off valve 21, a second on-off valve 22, a third on-off valve 23 and a fourth on-off valve 24, and specifically:

[0058] The first reversing valve 19 is used to realize the switching between the cooling mode and the heating mode, and the economizer 20 is used to improve the supercooling degree of the refrigerant and improve the performance of the compressor 12. The first reversing valve 19 and the economizer 20 are arranged in the second cavity 112, and the economizer 20 is arranged on the partition plate 16.

[0059] The first on-off valve 21 and the second on-off valve 22 are arranged corresponding to the second cavity 112. It can be understood that the arrangement corresponding to the second cavity 112 can be that the first on-off valve 21 and / or the second on-off valve 22 are located in the second cavity 112, or the first on-off valve 21 and / or the second on-off valve 22 are located outside the second cavity 112. As shown in Figure 7 One end of the first on-off valve 21 is connected with the first reversing valve 19, and the other end of the first on-off valve 21 is used to be connected with an external indoor unit 52. One end of the second on-off valve 22 is connected with the economizer 20, and the other end of the second on-off valve 22 is used to be connected with the external indoor unit 52.

[0060] The third switch valve 23 and the fourth switch valve 24 are arranged corresponding to the second cavity 112. It can be understood that the arrangement corresponding to the second cavity 112 can be that the third switch valve 23 and / or the fourth switch valve 24 are located in the second cavity 112, or the third switch valve 23 and / or the fourth switch valve 24 are located outside the second cavity 112. As shown in Figure 7 One end of the third switch valve 23 is connected with the outlet of the compressor 12, and the other end of the third switch valve 23 is used for being connected with the second refrigerant inlet 401 of the external hot water module. One end of the fourth switch valve 24 is connected with the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13, and the other end of the fourth switch valve 24 is used for being connected with the third refrigerant outlet 402 of the external hot water module.

[0061] As shown in Figure 7 The first switch valve 21, the second switch valve 22, the third switch valve 23 and the fourth switch valve 24 are arranged corresponding to the second cavity 112. It can be understood that the arrangement corresponding to the second cavity 112 can be that the first switch valve 21, the second switch valve 22, the third switch valve 23 and / or the fourth switch valve 24 are located in the second cavity 112, or the first switch valve 21, the second switch valve 22, the third switch valve 23 and / or the fourth switch valve 24 are located outside the second cavity 112. As shown in

[0062] For example, the first switch valve 21, the second switch valve 22, the third switch valve 23 and the fourth switch valve 24 are stop valves. Here, the four-way valve and the stop valve are only examples and do not limit the present application, and other valves can also be used.

[0063] As shown in Figure 3 The outdoor main unit further comprises a first throttling device 25. The first throttling device 25 is used for throttling and cooling the refrigerant, and is arranged in the second cavity 112. For example, the first throttling device 25 is an electronic expansion valve or a thermal expansion valve. Here, the electronic expansion valve and the thermal expansion valve are only examples and do not limit the present application, and other valves can also be used.

[0064] As shown in Figure 7As shown, the economizer 20 is a heat exchanger, which includes a third refrigerant port 201, a fourth refrigerant port 202, a fifth refrigerant port 203, and a sixth refrigerant port 204. The fourth refrigerant port 202 and the fifth refrigerant port 203 are connected to form an enthalpy-increasing main path, the fourth refrigerant port 202 is connected to the second switch valve 22, and one end of the first throttling device 25 is connected to a pipeline between the fourth refrigerant port 202 and the second switch valve 22. The other end of the first throttling device 25 is connected to the third refrigerant port 201 and the sixth refrigerant port 204 to form an enthalpy-increasing auxiliary path.

[0065] The air source heat pump system of the embodiment allows the refrigerant from the outdoor heat exchanger 17 to pass through the enthalpy-increasing main path (i.e., the fourth refrigerant port 202 and the fifth refrigerant port 203) to enter the indoor unit 52 and pass through the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201, and the sixth refrigerant port 204) to enter the inlet of the low-pressure gas-liquid separator 14. The refrigerant in the enthalpy-increasing auxiliary path is throttled and cooled by the first throttling device 25, and then absorbs heat from the refrigerant in the enthalpy-increasing main path in the economizer 20 more efficiently. After absorbing heat, the refrigerant vaporizes and enters the inlet of the low-pressure gas-liquid separator 14. Meanwhile, the refrigerant passing through the enthalpy-increasing main path is supercooled, and the temperature of the refrigerant entering the indoor unit 52 is lower, thereby improving the cooling effect in summer.

[0066] The air source heat pump system of the embodiment allows the refrigerant from the indoor unit 52 to pass through the enthalpy-increasing main path (i.e., the fourth refrigerant port 203 and the fifth refrigerant port 202) to enter the outdoor heat exchanger 17 and pass through the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201, and the sixth refrigerant port 204) to enter the enthalpy-increasing port 121 of the compressor 12. The refrigerant in the enthalpy-increasing auxiliary path is throttled and cooled by the first throttling device 25, and then absorbs heat from the refrigerant in the enthalpy-increasing main path in the economizer 20 more efficiently. After absorbing heat, the refrigerant vaporizes and enters the enthalpy-increasing port 121 of the compressor 12, thereby improving the performance of the compressor 12. Meanwhile, the refrigerant passing through the enthalpy-increasing main path is supercooled, and the temperature of the refrigerant entering the outdoor heat exchanger 17 is lower. In particular, in cold winter, the temperature of the refrigerant is lower than the outdoor temperature, thereby improving the heat absorption performance of the outdoor heat exchanger 17 in a low-temperature environment and improving the subsequent heating effect.

[0067] In some embodiments, as shown in FIG. 6, the economizer 20 is a heat exchanger, which includes a third refrigerant port 201, a fourth refrigerant port 202, a fifth refrigerant port 203, and a sixth refrigerant port 204. The fourth refrigerant port 202 and the fifth refrigerant port 203 are connected to form an enthalpy-increasing main path, the fourth refrigerant port 202 is connected to the second switch valve 22, and one end of the first throttling device 25 is connected to a pipeline between the fourth refrigerant port 202 and the second switch valve 22. The other end of the first throttling device 25 is connected to the third refrigerant port 201 and the sixth refrigerant port 204 to form an enthalpy-increasing auxiliary path.Figure 7 As shown, the outdoor main machine further comprises a fifth switch valve 26 and a sixth switch valve 27, which are arranged in the second cavity 112. The sixth refrigerant port 204 is connected to the enthalpy-increasing port 121 of the compressor 12 through the fifth switch valve 26, and is connected to the inlet of the low-pressure gas-liquid separator 14 through the sixth switch valve 27.

[0068] For example, the fifth switch valve 26 and the sixth switch valve 27 are solenoid valves. The solenoid valves are only examples and do not limit the present application. Other valves can also be used.

[0069] In some embodiments, as shown in Figure 2 and Figure 3 As shown, the outdoor main machine further comprises a fixed plate 28, which is arranged in the second cavity 112 and connected to the partition plate 16 and the shell 11. The first switch valve 21 and the second switch valve 22 are arranged on the fixed plate 28 and located in the second cavity 112. The third switch valve 23 and the fourth switch valve 24 are arranged on the shell 11 and located outside the second cavity 112.

[0070] In some embodiments, as shown in Figure 3 The first switch valve 21 and the second switch valve 22 are located below the first switch valve 19; and / or the third switch valve 23 and the fourth switch valve 24 are located above the first switch valve 19.

[0071] The first switch valve 19 is arranged at the middle position of the second cavity 112, and the positions below can just accommodate the compressor 12 and the low-pressure gas-liquid separator 14. The compressor 12 is more convenient to connect to the first switch valve 19, the high-pressure gas-liquid separator 13, and the electronic control module 15, etc.

[0072] In some embodiments, as shown in Figure 3 The outdoor main machine further comprises a seventh switch valve 29, which is arranged in the second cavity 112. As shown in Figure 7As shown, one end of the seventh switch valve 29 is connected with the outlet of the compressor 12, and the other end of the seventh switch valve 29 is connected with the third switch valve 23, and the seventh switch valve 29 is used for regulating the amount of refrigerant entering the external hot water module. For example, the seventh switch valve 29 is an electric two-way valve, which is only an example and does not limit the present application, and can also be other.

[0073] In some embodiments, as shown in Figure 3 As shown, the outdoor main machine further comprises a second reversing valve 30 arranged in the second cavity 112. As shown in Figure 7 As shown, the second reversing valve 30 is connected with the first refrigerant outlet 132 of the high-pressure gas-liquid separator 13, the outlet of the compressor 12 and the first valve port 191 of the first reversing valve 19, and the second reversing valve 30 is used for switching the whole heat or part of the heat of the refrigerant to exchange heat in the external hot water module.

[0074] As shown in Figure 7 As shown, the second reversing valve 30 comprises a fifth valve port 301, a sixth valve port 302 and a seventh valve port 303, the fifth valve port 301 is connected with the first refrigerant outlet 132 of the high-pressure gas-liquid separator 13, the sixth valve port 302 is connected with the first valve port 191 of the first reversing valve 19, and the seventh valve port 303 is connected with the outlet of the compressor 12.

[0075] For example, the second reversing valve 30 is a three-way valve, which is only an example and does not limit the present application, and can also be other.

[0076] In some embodiments, as shown in Figure 3 As shown, the outdoor main machine further comprises a second throttling device 31 arranged in the second cavity 112. As shown in Figure 7 As shown, one end of the second throttling device 31 is connected with the second refrigerant outlet 133 of the high-pressure gas-liquid separator 13, and the other end of the second throttling device 31 is connected with the fifth refrigerant port 203 of the economizer 20, and the second throttling device 31 is used for throttling and cooling the refrigerant. And the pipeline from one end of the second throttling device 31 to the second refrigerant outlet 133 of the high-pressure gas-liquid separator 13 is at least partially a capillary tube, that is Figure 7 As shown in 32.

[0077] For example, the second throttling device 31 is an electronic expansion valve or a thermal expansion valve, which is only an example and does not limit the present application, and can also be other.

[0078] In some embodiments, as shown in Figure 3As shown, the outdoor main machine further comprises a heat recovery branch 33, which is arranged in the second cavity 112. One way of the second refrigerant outlet 133 of the high-pressure gas-liquid separator 13 is connected with the fifth refrigerant port 203 of the economizer 20 through the second throttling device 31, and the other way of the second refrigerant outlet 133 of the high-pressure gas-liquid separator 13 is connected with the inlet of the low-pressure gas-liquid separator 14 through the heat recovery branch 33.

[0079] By arranging the heat recovery branch 33 between the second refrigerant outlet 133 of the high-pressure gas-liquid separator 13 and the inlet of the low-pressure gas-liquid separator 14, on one hand, the heat recovery branch 33 can realize the oil return of the oil accumulated in the high-pressure gas-liquid separator 13, and on the other hand, the heat recovery branch 33 can release the refrigerant migrated into the high-pressure gas-liquid separator 13 and perform pressure relief, so that the pressure balance of the system can be improved.

[0080] In some embodiments, as shown in Figure 7 As shown, the outdoor main machine further comprises an eighth switch valve 34, which is arranged on the heat recovery branch 33 and located in the second cavity 112. According to the system operation condition, the eighth switch valve 34 is opened to perform oil return or adjust the system pressure balance. At least part of the heat recovery branch 33 is a capillary tube, i.e. 35 shown in Figure 7 Due to the large resistance of the capillary tube, the capillary tube can be used to control the amount of refrigerant entering the low-pressure gas-liquid separator 14, so as to avoid that excessive refrigerant is relieved into the low-pressure gas-liquid separator 14 after the eighth switch valve 34 is opened.

[0081] For example, the eighth switch valve 34 is a solenoid valve. Here, the solenoid valve is only an example and does not limit the present application. The eighth switch valve 34 can also be other valves.

[0082] In some embodiments, as shown in Figure 4 As shown, the outdoor main machine further comprises a third throttling device 36 and a one-way valve 37, which are arranged in the second cavity 112. As shown in Figure 7 As shown, one way of the second refrigerant port 172 of the outdoor heat exchanger 17 is connected with the fifth refrigerant port 203 of the economizer 20 through the third throttling device 36, and the other way of the second refrigerant port 172 of the outdoor heat exchanger 17 is connected with the fifth refrigerant port 203 of the economizer 20 through the one-way valve 37, and the conduction direction of the one-way valve 37 is towards the fifth refrigerant port 203 of the economizer 20. It should be noted that the direction of the one-way valve 37 refers to the flow direction of the refrigerant, not the spatial position direction.

[0083] In some embodiments, as shown in Figure 3 andFigure 7 As shown, the outdoor main machine further comprises an oil separator 38 and an oil return pipe 39, the oil separator 38 is arranged at the outlet end of the compressor 12 and located in the second cavity 112, the oil separator 38 is used for separating the lubricating oil from the compressor 12 mixed in the refrigerant, and returning to the compressor 12 through the oil return pipe 39.

[0084] As shown in the drawings, Figure 7 Some embodiments of the utility model also disclose an air source heat pump system, which comprises the outdoor main machine in any of the above embodiments.

[0085] Some embodiments, as shown in the drawings, Figure 7 As shown in the drawings, the air source heat pump system further comprises a hot water module, the hot water module comprises a heat recovery heat exchanger 40, the heat recovery heat exchanger 40 is used for realizing heat storage of refrigerant and heat storage medium heat exchange, some embodiments are used for realizing heat exchange of refrigerant and water to produce domestic hot water, and the heat recovery heat exchanger 40 is a heat storage device with heat storage material in some other embodiments. The heat recovery heat exchanger 40 comprises a second refrigerant inlet 401 and a third refrigerant outlet 402, the second refrigerant inlet 401 is in communication with the third refrigerant outlet 402, the second refrigerant inlet 401 is connected with the third switch valve 23 of the outdoor main machine, and the third refrigerant outlet 402 is connected with the fourth switch valve 24 of the outdoor main machine.

[0086] When the heat pump system comprises the heat recovery heat exchanger 40, the system has multiple operation modes (see the following text for details), the high-pressure gas-liquid separator 13 can realize the automatic flow direction of refrigerant when switching between modes (mainly refrigeration and full heat recovery domestic hot water mode and refrigeration and waste heat recovery domestic hot water mode), thereby improving the stability of the system.

[0087] As shown in the drawings, Figure 7 As shown in the drawings, the heat recovery heat exchanger 40 further comprises a first water inlet 403 and a first water outlet 404, the first water inlet 403 is in communication with the first water outlet 404. The hot water module further comprises a domestic water tank 50, the domestic water tank 50 comprises a cold water inlet 501, a first water outlet 502, a first water return port 503 and a hot water outlet 504, the first water outlet 502 is connected with the first water inlet 403, and the first water outlet 404 is connected with the first water return port 503.

[0088] Some embodiments, as shown in the drawings, Figure 7As shown, the hot water module further comprises a first water pump 51, which is arranged in the water inlet pipeline of the heat recovery heat exchanger 40 (i.e. the pipeline connecting the first water outlet 502 and the first water inlet 403) or the water outlet pipeline (i.e. the pipeline connecting the first water outlet 404 and the first water return port 503), and is used to provide power for water circulation between the heat recovery heat exchanger 40 and the domestic water tank 50.

[0089] In some embodiments, as shown in Figure 7 As shown, the air source heat pump system further comprises at least one indoor unit 52, and it can be understood that the at least one indoor unit 52 can be one, two, three or any number. The indoor unit 52 is used to realize heat exchange between refrigerant and indoor air, and the indoor unit 52 comprises a seventh refrigerant port 521 and an eighth refrigerant port 522, the seventh refrigerant port 521 and the eighth refrigerant port 522 are in communication, the seventh refrigerant port 521 is connected with the first switch valve 21 of the outdoor main unit, and the eighth refrigerant port 522 is connected with the second switch valve 22 of the outdoor main unit.

[0090] In some embodiments, as shown in Figure 7 As shown, the air source heat pump system further comprises at least two indoor units 52, an air pipeline 53 and a liquid pipeline 54. Among them, in each indoor unit 52, the seventh refrigerant port 521 is connected with the corresponding tapping port in the air pipeline 53, and the eighth refrigerant port 522 is connected with the corresponding tapping port in the liquid pipeline 54. The total interface end of the liquid pipeline 54 is connected with the second switch valve 22 of the outdoor main unit, and the total interface end of the air pipeline 53 is connected with the first switch valve 21 of the outdoor main unit.

[0091] In some embodiments, as shown in Figure 7 As shown, the air source heat pump system further comprises a fourth throttling device 55, which is used to throttle and cool the refrigerant, and the eighth refrigerant port 522 is connected with the second switch valve 22 through the fourth throttling device 55. When there is a liquid pipeline 54, the eighth refrigerant port 522 is connected with the tapping port of the liquid pipeline 54 through the fourth throttling device 55.

[0092] In some embodiments, as shown in Figure 7As shown, the air source heat pump system further comprises at least one heat exchanger 56 for heat exchange between refrigerant and water in the terminal 58, the heat exchanger 56 comprises a ninth refrigerant port 561 and a tenth refrigerant port 562, the ninth refrigerant port 561 is in communication with the tenth refrigerant port 562. Wherein, the ninth refrigerant port 561 is connected with the corresponding tapping interface end in the gas pipe 53, and the tenth refrigerant port 562 is connected with the corresponding tapping interface end in the liquid pipe 54. Understandably, at least one can be one, two, three or any number.

[0093] In some embodiments, as shown in Figure 7 As shown, the air source heat pump system further comprises a fifth throttling device 57 for throttling and cooling the refrigerant. Wherein, the tenth refrigerant port 562 is connected with the corresponding tapping interface end in the liquid pipe 54 through the fifth throttling device 57. For example, the fifth throttling device 57 is an electronic expansion valve or a thermal expansion valve, which is only an example and does not limit the present application, and can also be other.

[0094] In some embodiments, as shown in Figure 7 As shown, the heat exchanger 56 further comprises a second water inlet 563 and a second water outlet 564, the second water inlet 563 is in communication with the second water outlet 564. The air source heat pump system further comprises the terminal 58, the terminal 58 comprises a second water outlet 581 and a second water inlet 582, the second water outlet 581 is connected with the second water inlet 563, and the second water outlet 564 is connected with the second water inlet 582. For example, the terminal 58 is a ground pipe, which realizes the effect of floor heating or ground cooling through heat exchange with the heat exchanger 56, and if the ground pipe is multi-way, the terminal can also be provided with a distribution water collector. Here, the ground pipe is only an example and does not limit the present application, and can also be other.

[0095] In some embodiments, as shown in Figure 8 As shown, the air source heat pump system further comprises a second water pump 59, which is arranged in the water inlet pipeline of the terminal 58 (i.e. the pipeline connecting the second water outlet 581 with the second water inlet 563) or the water outlet pipeline (i.e. the pipeline connecting the second water outlet 564 with the second water inlet 582), and the second water pump 59 is used to provide power for water circulation between the heat exchanger 56 and the terminal 58.

[0096] In some embodiments, as shown in Figure 7 As shown, the connection relationship between the components in the air source heat pump system is as follows:

[0097] One outlet of the compressor 12 is connected to the second refrigerant inlet 401 via the seventh switching valve 29 and the third switching valve 23. The other outlet of the compressor 12 is connected to the seventh valve port 303 of the second reversing valve 30. The third refrigerant outlet 402 is connected to the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 via the fourth switching valve 24. The first refrigerant outlet 132 of the high-pressure gas-liquid separator 13 is connected to the fifth valve port 301 of the second reversing valve 30. One outlet 133 of the high-pressure gas-liquid separator 13 is connected to the fifth refrigerant port 203 of the economizer 20 via the second throttling device 31. The other outlet 133 of the high-pressure gas-liquid separator 13 is connected to the inlet of the low-pressure gas-liquid separator 14 via the heat recovery branch 33. The sixth valve port 302 of the second reversing valve 30 is connected to the first valve port 191 of the first reversing valve 19. The second valve port 192 of the first reversing valve 19 is connected to the first refrigerant port 171 of the outdoor heat exchanger 17. The third valve port 193 of the first reversing valve 19 is connected to the inlet of the low-pressure gas-liquid separator 14, and the outlet of the low-pressure gas-liquid separator 14 is connected to the inlet of the compressor 12. The fourth valve port 194 of the first reversing valve 19 is connected to the main interface of the gas pipe 53 via the first switching valve 21. The main interface of the liquid pipe 54 is connected to the fourth refrigerant port 202 of the economizer 20 via the second switching valve 22, and another path of the main interface of the liquid pipe 54 is connected to the third refrigerant port 201 of the economizer 20 via the first throttling device 25. The fifth refrigerant port 203 of the economizer 20 is connected via the third throttling device 36 to the second refrigerant port 172 of the outdoor heat exchanger 17. The other path of the fifth refrigerant port 203 is connected via the one-way valve 37 to the second refrigerant port 172 of the outdoor heat exchanger 17. The one-way valve 37 is directed towards the fifth refrigerant port 203 of the economizer 20. The sixth refrigerant port 204 of the economizer 20 is connected via the sixth switching valve 27 to the inlet of the low-pressure gas-liquid separator 14. The other path of the sixth refrigerant port 204 is connected via the fifth switching valve 26 to the enthalpy-increasing port 121 of the compressor 12.

[0098] The first outlet 502 of the domestic water tank 50 is connected to the first water inlet 403 of the heat recovery heat exchanger 40 via the first water pump 51, and the first water outlet 404 of the heat recovery heat exchanger 40 is connected to the first return water inlet 503 of the domestic water tank 50.

[0099] The seventh refrigerant port 521 of the indoor unit 52 is connected to the corresponding tapping end in the gas pipe 53, and the eighth refrigerant port 522 of the indoor unit 52 is connected to the corresponding tapping end in the liquid pipe 54 through the fourth throttling device 55.

[0100] The ninth refrigerant port 561 of the heat exchanger 56 is connected to the corresponding tapping end in the gas pipe 53, and the tenth refrigerant port 562 of the heat exchanger 56 is connected to the corresponding tapping end in the liquid pipe 54 through the fifth throttling device 57. The second water outlet 581 of the terminal 58 is connected to the second water inlet 563 of the heat exchanger 56 through the second water pump 59, and the second water outlet 564 of the heat exchanger 56 is connected to the second water return port 582 of the terminal 58.

[0101] In different cases, the air source heat pump system corresponds to different valve port communications. The refrigerant flow directions of each mode are shown in the following figures. It should be noted that the components not mentioned to be opened are closed. The specific conditions are as follows:

[0102] As Figure 8As shown, in the refrigeration and full heat recovery hot water mode, the second throttling device 31, the fourth throttling device 55, the fifth throttling device 57, the first switch valve 21, the second switch valve 22, the third switch valve 23, the fourth switch valve 24, the sixth switch valve 27 and the seventh switch valve 29 are opened, the fifth valve port 301 of the second reversing valve 30 is connected with the sixth valve port 302 or not connected, and the fourth valve port 194 of the first reversing valve 19 is connected with the third valve port 193. That is, when hot water needs to be prepared quickly in the refrigeration mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the second refrigerant inlet 401 of the heat recovery heat exchanger 40 through the seventh switch valve 29 and the third switch valve 23, exchanges heat with the water in the water tank 50 in the heat recovery heat exchanger 40, and becomes medium-temperature liquid refrigerant after preparing hot water, the medium-temperature liquid refrigerant output from the third refrigerant outlet 402 of the heat recovery heat exchanger 40 enters the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 through the fourth switch valve 24, and is separated into gas and liquid in the high-pressure gas-liquid separator 13 to ensure that the refrigerant output from the second refrigerant outlet 133 is pure liquid. The medium-temperature liquid refrigerant output from the second refrigerant outlet 133 becomes low-temperature liquid refrigerant with a lower temperature after being throttled by the second throttling device 31, and then enters the enthalpy-increasing main path (i.e., the fifth refrigerant port 203 and the fourth refrigerant port 202), the low-temperature liquid refrigerant output from the enthalpy-increasing main path enters the liquid pipe 54 through the second switch valve 22, and the low-temperature liquid refrigerant output from the enthalpy-increasing main path of the economizer 20 enters the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201 and the fifth refrigerant port 203), the low-temperature liquid refrigerant in the enthalpy-increasing auxiliary path is throttled by the first throttling device 25 to become low-temperature gaseous refrigerant, which can more efficiently absorb heat from the refrigerant in the enthalpy-increasing main path in the economizer 20, and the low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary path returns to the inlet of the compressor 12 through the sixth switch valve 27 and the low-pressure gas-liquid separator 14. The low-temperature liquid refrigerant in the enthalpy-increasing main path becomes low-temperature liquid refrigerant with a lower temperature after heat exchange, enters the fourth throttling device 55 in the liquid pipe 54, becomes low-temperature liquid refrigerant with a lower temperature after being throttled by the fourth throttling device 55, and then enters the eighth refrigerant port 522 of the indoor unit 52, the low-temperature liquid refrigerant exchanges heat with indoor air in the indoor unit 52, and the low-temperature liquid refrigerant absorbs heat from the indoor air to evaporate into low-temperature gaseous refrigerant, the indoor unit 52 blows cold air, and the low-temperature gaseous refrigerant output from the seventh refrigerant port 521 of the indoor unit 52 enters the gas pipe 53.And, the low-temperature liquid refrigerant in the liquid pipe 54 enters the fifth throttling device 57, and after being throttled and cooled by the fifth throttling device 57, becomes low-temperature liquid refrigerant with a lower temperature, and then enters the tenth refrigerant port 562 of the heat exchanger 56. The low-temperature liquid refrigerant exchanges heat with the water in the terminal 58 in the heat exchanger 56, and after absorbing the heat of the water, evaporates into low-temperature gaseous refrigerant. The water in the terminal 58 becomes cold water, and the low-temperature gaseous refrigerant output by the ninth refrigerant port 561 of the heat exchanger 56 enters the gas pipe 53. The low-temperature gaseous refrigerant output by the gas pipe 53, after passing through the first switch valve 21, the fourth valve port 194 and the third valve port 193 of the first reversing valve 19, and the low-pressure gas-liquid separator 14, returns to the inlet of the compressor 12, and reciprocates.

[0103] The heat recovery heat exchanger 40 is connected to the domestic water tank 50, so that all the condensation heat originally used for heat exchange with air by the outdoor heat exchanger 17 is recovered during refrigeration, avoiding the waste of heat exchange between the outdoor heat exchanger 17 and air. The recovered heat is exchanged with the water in the domestic water tank 50 in the heat recovery heat exchanger 40, so that hot water is quickly prepared, the energy utilization rate is improved, and the hot water preparation speed is improved. And by configuring the heat exchanger 56 and the terminal 58, the effect of ground cooling and the like can be achieved during refrigeration, and the energy utilization rate is improved.

[0104] As Figure 9As shown, when the domestic hot water reaches a certain temperature, it can be switched to a cooling and waste heat recovery domestic hot water mode. In the cooling and waste heat recovery domestic hot water mode, the fourth throttling device 55, the fifth throttling device 57, the first switching valve 21, the second switching valve 22, the third switching valve 23, the fourth switching valve 24, the sixth switching valve 27, and the seventh switching valve 29 are opened. The fifth valve port 301 of the second reversing valve 30 is connected to the sixth valve port 302. The first valve port 191 of the first reversing valve 19 is connected to the second valve port 192. The fourth valve port 194 of the first reversing valve 19 is connected to the third valve port 193. That is, when hot water needs to be prepared in cooling mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the second refrigerant inlet 401 of the heat recovery heat exchanger 40 after passing through the seventh switch valve 29 and the third switch valve 23. The high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 50 in the heat recovery heat exchanger 40, and becomes a medium-temperature gaseous refrigerant after preparing hot water. The medium-temperature gaseous refrigerant output from the third refrigerant outlet 402 of the heat recovery heat exchanger 40 enters the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 through the fourth switch valve 24, and gas-liquid separation is carried out in the high-pressure gas-liquid separator 13 to ensure that the refrigerant output from the first refrigerant outlet 132 is pure gaseous. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 132 enters the first refrigerant port 171 of the outdoor heat exchanger 17 after passing through the fifth valve port 301 and the sixth valve port 302 of the second reversing valve 30 and the first valve port 191 and the second valve port 192 of the first reversing valve 19. The medium-temperature gaseous refrigerant condenses and releases heat in the outdoor heat exchanger 17 and becomes a medium-temperature liquid refrigerant. The medium-temperature liquid refrigerant output from the second refrigerant port 172 of the outdoor heat exchanger 17 enters the enthalpy-increasing main circuit (i.e., the fifth refrigerant port 203 and the fourth refrigerant port 202) through the one-way valve 37. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit enters the liquid pipe 54 through the second switching valve 22. The medium-temperature liquid refrigerant output from the enthalpy-increasing main circuit of the economizer 20 enters the enthalpy-increasing auxiliary circuit (i.e., the first throttling device 25, the third refrigerant port 201, and the fifth refrigerant port 203). After being throttled and cooled by the first throttling device 25 in the enthalpy-increasing auxiliary circuit, the medium-temperature liquid refrigerant can absorb the refrigerant heat from the enthalpy-increasing main circuit more efficiently in the economizer 20 and become a low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary circuit returns to the inlet of the compressor 12 after passing through the sixth switching valve 27 and the low-pressure gas-liquid separator 14.The medium-temperature liquid refrigerant of the enthalpy-increasing main path is reduced in temperature by heat exchange to become low-temperature liquid refrigerant of even lower temperature. The low-temperature liquid refrigerant output by the enthalpy-increasing main path enters the liquid pipe 54 via the second switch valve 22. The low-temperature liquid refrigerant output by the enthalpy-increasing main path of the economizer 20 enters the enthalpy-increasing auxiliary path. The medium-temperature liquid refrigerant or the low-temperature liquid refrigerant enters the fourth throttling device 55 in the liquid pipe 54, is reduced in temperature by throttling of the fourth throttling device 55, becomes low-temperature liquid refrigerant of even lower temperature, and then enters the eighth refrigerant port 522 of the indoor unit 52. The low-temperature liquid refrigerant exchanges heat with indoor air in the indoor unit 52, is evaporated to become low-temperature gaseous refrigerant after absorbing heat from the indoor air, and the indoor unit 52 blows out cold air. The low-temperature gaseous refrigerant output by the seventh refrigerant port 521 of the indoor unit 52 enters the gas pipe 53. Also, the medium-temperature liquid refrigerant or the low-temperature liquid refrigerant enters the fifth throttling device 57 in the liquid pipe 54, is reduced in temperature by throttling of the fifth throttling device 57, becomes low-temperature liquid refrigerant of even lower temperature, and then enters the tenth refrigerant port 562 of the heat exchanger 56. The low-temperature liquid refrigerant exchanges heat with water in the terminal 58 in the heat exchanger 56, is evaporated to become low-temperature gaseous refrigerant after absorbing heat from the water, and the water in the terminal 58 becomes cold water. The low-temperature gaseous refrigerant output by the ninth refrigerant port 561 of the heat exchanger 56 enters the gas pipe 53. The low-temperature gaseous refrigerant output by the gas pipe 53 returns to the inlet of the compressor 12 via the first switch valve 21, the fourth valve port 194 and the third valve port 193 of the first reversing valve 19, and the low-pressure gas-liquid separator 14, and circulates repeatedly.

[0105] The heat recovery heat exchanger 40 is connected to the domestic water tank 50, so that at least part of the condensation heat originally used for heat exchange with air by the outdoor heat exchanger 17 is recovered during refrigeration, avoiding waste of heat by heat exchange between the outdoor heat exchanger 17 and air. The recovered heat is exchanged with water in the domestic water tank 50 in the heat recovery heat exchanger 40, hot water is prepared quickly, energy utilization rate is improved, and heating speed is improved. Also, by arranging the heat exchanger 56 and the terminal 58, ground cooling and other effects can be achieved during refrigeration, and energy utilization rate is improved.

[0106] Specifically, Figure 9 and Figure 8 The difference between the embodiments shown in Figs. 1 and 2 is that, Figure 9 at least part of the condensation heat originally used for heat exchange with air by the outdoor heat exchanger 17 is recovered during refrigeration, and Figure 8 all of the condensation heat originally used for heat exchange with air by the outdoor heat exchanger 17 is recovered during refrigeration.

[0107] As Figure 10As shown, in the refrigeration and waste heat recovery mode, the fourth throttling device 55, the fifth throttling device 57, the first switch valve 21, the second switch valve 22, the third switch valve 23, the fourth switch valve 24, the sixth switch valve 27 and the seventh switch valve 29 are opened, the sixth valve port 302 of the second reversing valve 30 is connected with the fifth valve port 301 and the seventh valve port 303, the first valve port 191 of the first reversing valve 19 is connected with the second valve port 192, and the fourth valve port 194 of the first reversing valve 19 is connected with the third valve port 193. That is, when hot water is needed in the refrigeration mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the second refrigerant inlet 401 of the heat recovery heat exchanger 40 through the seventh switch valve 29 and the third switch valve 23, and the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the first refrigerant port 171 of the outdoor heat exchanger 17 through the seventh valve port 303 and the sixth valve port 302 of the second reversing valve 30 and the first valve port 191 and the second valve port 192 of the first reversing valve 19. The high-temperature gaseous refrigerant exchanges heat with the water in the water tank 50 in the heat recovery heat exchanger 40, becomes medium-temperature gaseous refrigerant after preparing hot water, and the medium-temperature gaseous refrigerant output from the third refrigerant outlet 402 of the heat recovery heat exchanger 40 enters the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 through the fourth switch valve 24, is subjected to gas-liquid separation in the high-pressure gas-liquid separator 13, and ensures that the refrigerant output from the first refrigerant outlet 132 is pure gaseous. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 132 enters the first refrigerant port 171 of the outdoor heat exchanger 17 through the fifth valve port 301 and the sixth valve port 302 of the second reversing valve 30 and the first valve port 191 and the second valve port 192 of the first reversing valve 19, and becomes medium-temperature liquid refrigerant after condensing and releasing heat in the outdoor heat exchanger 17. The medium-temperature liquid refrigerant output from the second refrigerant port 172 of the outdoor heat exchanger 17 enters the enthalpy-increasing main path (i.e., the fifth refrigerant port 203 and the fourth refrigerant port 202) through the one-way valve 37, the medium-temperature liquid refrigerant output from the enthalpy-increasing main path enters the liquid pipe 54 through the second switch valve 22, the medium-temperature liquid refrigerant output from the enthalpy-increasing main path of the economizer 20 enters the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201 and the fifth refrigerant port 203), the medium-temperature liquid refrigerant is throttled and cooled by the first throttling device 25 in the enthalpy-increasing auxiliary path, and can more efficiently absorb heat from the refrigerant in the enthalpy-increasing main path in the economizer 20 to become low-temperature gaseous refrigerant, and the low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary path returns to the inlet of the compressor 12 through the sixth switch valve 27 and the low-pressure gas-liquid separator 14.The medium-temperature liquid refrigerant of the enthalpy-increasing main path is reduced in temperature by heat exchange to become low-temperature liquid refrigerant with even lower temperature. The low-temperature liquid refrigerant output by the enthalpy-increasing main path of the economizer 20 enters the liquid pipe 54 via the second switch valve 22. The low-temperature liquid refrigerant output by the enthalpy-increasing main path of the economizer 20 enters the enthalpy-increasing auxiliary path. The medium-temperature liquid refrigerant or the low-temperature liquid refrigerant enters the fourth throttling device 55 in the liquid pipe 54, is reduced in temperature by throttling of the fourth throttling device 55, becomes low-temperature liquid refrigerant with even lower temperature, and then enters the eighth refrigerant port 522 of the indoor unit 52. The low-temperature liquid refrigerant exchanges heat with indoor air in the indoor unit 52, is evaporated to become low-temperature gaseous refrigerant after absorbing heat from the indoor air, and the indoor unit 52 blows out cold air. The low-temperature gaseous refrigerant output by the seventh refrigerant port 521 of the indoor unit 52 enters the gas pipe 53. Also, the medium-temperature liquid refrigerant or the low-temperature liquid refrigerant enters the fifth throttling device 57 in the liquid pipe 54, is reduced in temperature by throttling of the fifth throttling device 57, becomes low-temperature liquid refrigerant with even lower temperature, and then enters the tenth refrigerant port 562 of the heat exchanger 56. The low-temperature liquid refrigerant exchanges heat with water in the terminal 58 in the heat exchanger 56, is evaporated to become low-temperature gaseous refrigerant after absorbing heat from the water, and the water in the terminal 58 becomes cold water. The low-temperature gaseous refrigerant output by the ninth refrigerant port 561 of the heat exchanger 56 enters the gas pipe 53. The low-temperature gaseous refrigerant output by the gas pipe 53 returns to the inlet of the compressor 12 via the first switch valve 21, the fourth valve port 194 and the third valve port 193 of the first reversing valve 19, and the low-pressure gas-liquid separator 14, and circulates repeatedly.

[0108] Specifically, Figure 10 and Figure 9 The difference between the embodiments shown in FIGS. 1 and 2 is that, Figure 10 In the embodiment shown in FIG. 2, one more path of refrigerant enters the outdoor heat exchanger 17 via the seventh valve port 303 and the sixth valve port 302 of the second reversing valve 30 and the first valve port 191 and the second valve port 192 of the first reversing valve 19, which can better control the amount of refrigerant entering the heat recovery heat exchanger 40, and the refrigerant coming out of the compressor 12 directly to the first reversing valve 19 can be more guaranteed to be pure gaseous refrigerant, and the pure gaseous refrigerant can more guarantee that the first reversing valve 19 has sufficient pressure difference for reversing, so the pressure loss of the refrigerant pipeline is smaller.

[0109] As Figure 11As shown, in the heating and hot water mode, the first throttling device 25, the third throttling device 36, the fourth throttling device 55, the fifth throttling device 57, the first on-off valve 21, the second on-off valve 22, the third on-off valve 23, the fourth on-off valve 24, the fifth on-off valve 26 and the seventh on-off valve 29 are opened, the fifth valve port 301 of the second reversing valve 30 is communicated with the sixth valve port 302, the first valve port 191 of the first reversing valve 19 is communicated with the fourth valve port 194, and the second valve port 192 of the first reversing valve 19 is communicated with the third valve port 193. That is, when hot water needs to be prepared in the heating mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the second refrigerant inlet 401 of the heat recovery heat exchanger 40 through the seventh on-off valve 29 and the third on-off valve 23, exchanges heat with the water in the water tank 50 in the heat recovery heat exchanger 40, and becomes medium-temperature gaseous refrigerant after preparing hot water. The medium-temperature gaseous refrigerant output from the third refrigerant outlet 402 of the heat recovery heat exchanger 40 enters the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 through the fourth on-off valve 24, and is separated into gas and liquid in the high-pressure gas-liquid separator 13 to ensure that the refrigerant output from the first refrigerant outlet 132 is pure gas. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 132 enters the gas pipe 53 through the fifth valve port 301 and the sixth valve port 302 of the second reversing valve 30, the first valve port 191 and the fourth valve port 194 of the first reversing valve 19, and the first on-off valve 21, enters the seventh refrigerant port 521 of the indoor unit 52 in the gas pipe 53, exchanges heat with indoor air in the indoor unit 52, and condenses into medium-temperature liquid refrigerant after releasing heat to the indoor air. The indoor unit 52 blows hot air, and the medium-temperature liquid refrigerant output from the eighth refrigerant port 522 of the indoor unit 52 becomes low-temperature liquid refrigerant after throttling and cooling by the fourth throttling device 55, and then the low-temperature liquid refrigerant output from the fourth throttling device 55 enters the liquid pipe 54. Moreover, the medium-temperature gaseous refrigerant enters the ninth refrigerant port 561 of the heat exchanger 56 in the gas pipe 53, exchanges heat with the water in the terminal 58 in the heat exchanger 56, and becomes medium-temperature liquid refrigerant, and the water in the terminal 58 becomes hot water. The medium-temperature liquid refrigerant output from the tenth refrigerant port 562 of the heat exchanger 56 becomes low-temperature liquid refrigerant after throttling and cooling by the fifth throttling device 57, and then the low-temperature liquid refrigerant output from the fifth throttling device 57 enters the liquid pipe 54.The low-temperature liquid refrigerant output by the liquid pipe 54 enters the enthalpy-increasing main path (i.e. the fourth refrigerant port 202 and the fifth refrigerant port 203) through the second switch valve 22, and enters the enthalpy-increasing auxiliary path (i.e. the first throttling device 25, the third refrigerant port 201 and the fifth refrigerant port 203) through the second switch valve 22. The low-temperature liquid refrigerant in the enthalpy-increasing auxiliary path is throttled by the first throttling device 25 to become low-temperature gaseous refrigerant, which is more efficiently absorbed by the economizer 20 from the enthalpy-increasing main path to become low-temperature gaseous refrigerant, and is output by the fifth switch valve 26 to the enthalpy-increasing port 121 of the compressor 12. The low-temperature liquid refrigerant in the enthalpy-increasing main path is cooled by heat exchange to become low-temperature liquid refrigerant, and is throttled by the third throttling device 36 to become low-temperature liquid refrigerant, and is input into the second refrigerant port 172 of the outdoor heat exchanger 17. The low-temperature liquid refrigerant in the outdoor heat exchanger 17 is evaporated to become low-temperature gaseous refrigerant, and is output by the first refrigerant port 171 of the outdoor heat exchanger 17 to the second valve port 192 and the third valve port 193 of the first switch valve 19, and is output to the inlet of the compressor 12 through the low-pressure gas-liquid separator 14, and is circulated repeatedly. The air source heat pump system can produce hot water and realize floor heating and other effects while heating, and improves energy utilization.

[0110] As Figure 12As shown, in the heating and hot water mode, the first throttling device 25, the third throttling device 36, the fourth throttling device 55, the fifth throttling device 57, the first on-off valve 21, the second on-off valve 22, the third on-off valve 23, the fourth on-off valve 24, the fifth on-off valve 26 and the seventh on-off valve 29 are opened, the sixth valve port 302 of the second reversing valve 30 is communicated with the fifth valve port 301 and the seventh valve port 303, the first valve port 191 of the first reversing valve 19 is communicated with the fourth valve port 194, and the second valve port 192 of the first reversing valve 19 is communicated with the third valve port 193. That is, when hot water needs to be prepared in the heating mode, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the second refrigerant inlet 401 of the heat recovery heat exchanger 40 through the seventh on-off valve 29 and the third on-off valve 23, and the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the gas pipe 53 through the seventh valve port 303 and the sixth valve port 302 of the second reversing valve 30, the first valve port 191 and the fourth valve port 194 of the first reversing valve 19, and the first on-off valve 21. The high-temperature gaseous refrigerant exchanges heat with the water in the hot water tank 50 in the heat recovery heat exchanger 40, becomes medium-temperature gaseous refrigerant after preparing hot water, and the medium-temperature gaseous refrigerant output from the third refrigerant outlet 402 of the heat recovery heat exchanger 40 enters the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 through the fourth on-off valve 24, and is separated into gas and liquid in the high-pressure gas-liquid separator 13 to ensure that the refrigerant output from the first refrigerant outlet 132 is pure gas. The medium-temperature gaseous refrigerant output from the first refrigerant outlet 132 enters the gas pipe 53 through the fifth valve port 301 and the sixth valve port 302 of the second reversing valve 30, the first valve port 191 and the fourth valve port 194 of the first reversing valve 19, and the first on-off valve 21, and enters the seventh refrigerant port 521 of the indoor unit 52 in the gas pipe 53. The medium-temperature gaseous refrigerant exchanges heat with indoor air in the indoor unit 52, and the medium-temperature gaseous refrigerant condenses into medium-temperature liquid refrigerant after releasing heat to the indoor air. The indoor unit 52 blows hot air, and the medium-temperature liquid refrigerant output from the eighth refrigerant port 522 of the indoor unit 52 becomes low-temperature liquid refrigerant after throttling and cooling by the fourth throttling device 55, and then the low-temperature liquid refrigerant output from the fourth throttling device 55 enters the liquid pipe 54. Moreover, the medium-temperature gaseous refrigerant enters the ninth refrigerant port 561 of the heat exchanger 56 in the gas pipe 53, exchanges heat with the water in the terminal 58 in the heat exchanger 56, and becomes medium-temperature liquid refrigerant, and the water in the terminal 58 becomes hot water. The medium-temperature liquid refrigerant output from the tenth refrigerant port 562 of the heat exchanger 56 becomes low-temperature liquid refrigerant after throttling and cooling by the fifth throttling device 57, and then the low-temperature liquid refrigerant output from the fifth throttling device 57 enters the liquid pipe 54.The low-temperature liquid refrigerant output by the liquid pipe 54 enters the second switch valve 22 and then enters the enthalpy-increasing main path (i.e., the fourth refrigerant port 202 and the fifth refrigerant port 203) through one path, and enters the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201 and the fifth refrigerant port 203) through another path. After being throttled and cooled by the first throttling device 25, the low-temperature liquid refrigerant in the enthalpy-increasing auxiliary path can more efficiently absorb the heat of the refrigerant from the enthalpy-increasing main path in the economizer 20, and become low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output by the enthalpy-increasing auxiliary path returns to the enthalpy-increasing port 121 of the compressor 12 through the fifth switch valve 26. The low-temperature liquid refrigerant in the enthalpy-increasing main path is cooled by heat exchange and becomes low-temperature liquid refrigerant with a lower temperature, and then enters the third throttling device 36 for throttling and cooling, and becomes low-temperature liquid refrigerant with a lower temperature. The low-temperature liquid refrigerant enters the second refrigerant port 172 of the outdoor heat exchanger 17, and after being evaporated and absorbing heat in the outdoor heat exchanger 17, becomes low-temperature gaseous refrigerant. The low-temperature gaseous refrigerant output by the first refrigerant port 171 of the outdoor heat exchanger 17 returns to the inlet of the compressor 12 through the second valve port 192 and the third valve port 193 of the first reversing valve 19 and the low-pressure gas-liquid separator 14, and reciprocates.

[0111] Specifically, Figure 12 and Figure 11 The difference between the embodiment shown in the figure and the embodiment shown in the figure is that Figure 12 In the embodiment shown in the figure, the seventh valve port 303 and the sixth valve port 302 of the second reversing valve 30, the first valve port 191 and the fourth valve port 194 of the first reversing valve 19, and the second switch valve 22 enter the gas pipe 53, which can better control the amount of refrigerant entering the heat recovery heat exchanger 40, and the refrigerant directly from the compressor to the first reversing valve 19 can ensure that the refrigerant is gaseous, and the pure gaseous refrigerant can more ensure that the first reversing valve 19 has enough pressure difference for reversing, so the pressure loss of the refrigerant pipeline is smaller.

[0112] As Figure 13As shown, in the pure hot water mode, the second throttling device 31, the third throttling device 36, the third switch valve 23, the fourth switch valve 24 and the seventh switch valve 29 are opened, the fifth valve port 301 and the sixth valve port 302 of the second reversing valve 30 are connected or not connected, and the second valve port 192 and the third valve port 193 of the first reversing valve 19 are connected. That is, when only hot water needs to be prepared, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the second refrigerant inlet 401 of the heat recovery heat exchanger 40 through the seventh switch valve 29 and the third switch valve 23, and the high-temperature gaseous refrigerant exchanges heat with the water in the domestic water tank 50 in the heat recovery heat exchanger 40, and becomes medium-temperature liquid refrigerant after preparing hot water. The medium-temperature liquid refrigerant output from the third refrigerant outlet 402 of the heat recovery heat exchanger 40 enters the first refrigerant inlet 131 of the high-pressure gas-liquid separator 13 through the fourth switch valve 24, and is subjected to gas-liquid separation in the high-pressure gas-liquid separator 13 to ensure that the refrigerant output from the second refrigerant outlet 133 is pure liquid. The medium-temperature liquid refrigerant output from the second refrigerant outlet 133 is throttled and cooled by the second throttling device 31 to become low-temperature liquid refrigerant with a lower temperature, and then enters the third throttling device 36 for further throttling and cooling, and becomes low-temperature liquid refrigerant with a lower temperature, and then enters the second refrigerant port 172 of the outdoor heat exchanger 17. The low-temperature liquid refrigerant evaporates and absorbs heat in the outdoor heat exchanger 17 to become low-temperature gaseous refrigerant, and the low-temperature gaseous refrigerant output from the first refrigerant port 171 of the outdoor heat exchanger 17 returns to the inlet of the compressor 12 through the second valve port 192 and the third valve port 193 of the first reversing valve 19 and the low-pressure gas-liquid separator 14, and reciprocates.

[0113] As Figure 14As shown, in the cooling mode, the first throttling device 25, the fourth throttling device 55, the fifth throttling device 57, the first switch valve 21, the second switch valve 22 and the sixth switch valve 27 are opened, the seventh valve port 303 of the second reversing valve 30 is communicated with the sixth valve port 302, the first valve port 191 of the first reversing valve 19 is communicated with the second valve port 192, and the fourth valve port 194 of the first reversing valve 19 is communicated with the third valve port 193. That is, when cooling in summer, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the first refrigerant port 171 of the outdoor heat exchanger 17 through the seventh valve port 303 and the sixth valve port 302 of the second reversing valve 30 and the first valve port 191 and the second valve port 192 of the first reversing valve 19, and the medium-temperature gaseous refrigerant becomes medium-temperature liquid refrigerant after being condensed and releasing heat in the outdoor heat exchanger 17. The medium-temperature liquid refrigerant output from the second refrigerant port 172 of the outdoor heat exchanger 17 enters the enthalpy-increasing main path (i.e., the fifth refrigerant port 203 and the fourth refrigerant port 202) through the check valve 37, the medium-temperature liquid refrigerant output from the enthalpy-increasing main path enters the liquid pipe 54 through the second switch valve 22, and the medium-temperature liquid refrigerant output from the enthalpy-increasing main path of the economizer 20 enters the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201 and the fifth refrigerant port 203). After being throttled and cooled by the first throttling device 25 in the enthalpy-increasing auxiliary path, the medium-temperature liquid refrigerant can more efficiently absorb the heat of the refrigerant from the enthalpy-increasing main path in the economizer 20 to become low-temperature gaseous refrigerant, which enters the inlet of the compressor 12 through the sixth switch valve 27 and the low-pressure gas-liquid separator 14. The medium-temperature liquid refrigerant in the enthalpy-increasing main path becomes low-temperature liquid refrigerant with a lower temperature after heat exchange, the low-temperature liquid refrigerant output from the enthalpy-increasing main path enters the liquid pipe 54 through the second switch valve 22, and the low-temperature liquid refrigerant output from the enthalpy-increasing main path of the economizer 20 enters the enthalpy-increasing auxiliary path. The medium-temperature liquid refrigerant or the low-temperature liquid refrigerant enters the fourth throttling device 55 in the liquid pipe 54, becomes low-temperature liquid refrigerant with a lower temperature after being throttled and cooled by the fourth throttling device 55, and then enters the eighth refrigerant port 522 of the indoor unit 52. The low-temperature liquid refrigerant exchanges heat with indoor air in the indoor unit 52, and the low-temperature liquid refrigerant absorbs heat from the indoor air to evaporate and become low-temperature gaseous refrigerant, the indoor unit 52 blows cold air, and the low-temperature gaseous refrigerant output from the seventh refrigerant port 521 of the indoor unit 52 enters the gas pipe 53.And, the medium temperature liquid refrigerant or the low temperature liquid refrigerant enters into the fifth throttling device 57 in the liquid pipe 54, becomes the low temperature liquid refrigerant with lower temperature after the temperature reduction of the fifth throttling device 57, then enters into the tenth refrigerant port 562 of the heat exchanger 56, the low temperature liquid refrigerant exchanges heat with the water in the terminal 58 in the heat exchanger 56, the low temperature liquid refrigerant evaporates into the low temperature gaseous refrigerant after absorbing the heat of the water, the water in the terminal 58 becomes the cold water, the low temperature gaseous refrigerant outputted by the ninth refrigerant port 561 of the heat exchanger 56 enters into the gas pipe 53. The low temperature gaseous refrigerant outputted by the gas pipe 53 returns to the inlet of the compressor 12 after the first switch valve 21, the fourth valve port 194 and the third valve port 193 of the first reversing valve 19 and the low pressure gas-liquid separator 14, reciprocating circulation. The air source heat pump system can realize the ground cooling effect and the like while refrigerating, improving the energy utilization rate.

[0114] As Figure 15As shown, in the heating mode, the first throttling device 25, the third throttling device 36, the fourth throttling device 55, the fifth throttling device 57, the first on-off valve 21, the second on-off valve 22 and the fifth on-off valve 26 are opened, the sixth valve port 302 of the second reversing valve 30 is communicated with the seventh valve port 303, the first valve port 191 of the first reversing valve 19 is communicated with the fourth valve port 194, and the second valve port 192 of the first reversing valve 19 is communicated with the third valve port 193. That is, when heating in winter, the high-temperature gaseous refrigerant output from the outlet of the compressor 12 enters the gas pipe 53 through the seventh valve port 303 and the sixth valve port 302 of the second reversing valve 30, the first valve port 191 and the fourth valve port 194 of the first reversing valve 19, and the first on-off valve 21, the medium-temperature gaseous refrigerant enters the seventh refrigerant port 521 of the indoor unit 52 in the gas pipe 53, the medium-temperature gaseous refrigerant exchanges heat with indoor air in the indoor unit 52, and the medium-temperature gaseous refrigerant releases heat to the indoor air and then condenses into medium-temperature liquid refrigerant, the indoor unit 52 blows out hot air, and the medium-temperature liquid refrigerant output from the eighth refrigerant port 522 of the indoor unit 52 becomes low-temperature liquid refrigerant after throttling and cooling by the fourth throttling device 55, and then the low-temperature liquid refrigerant output from the fourth throttling device 55 enters the liquid pipe 54. Moreover, the medium-temperature gaseous refrigerant enters the ninth refrigerant port 561 of the heat exchanger 56 in the gas pipe 53, the medium-temperature gaseous refrigerant exchanges heat with water in the terminal 58 in the heat exchanger 56 and then becomes medium-temperature liquid refrigerant, and the water in the terminal 58 becomes hot water, the medium-temperature liquid refrigerant output from the tenth refrigerant port 562 of the heat exchanger 56 becomes low-temperature liquid refrigerant after throttling and cooling by the fifth throttling device 57, and then the low-temperature liquid refrigerant output from the fifth throttling device 57 enters the liquid pipe 54. The low-temperature liquid refrigerant output from the liquid pipe 54 enters the enthalpy-increasing main path (i.e., the fourth refrigerant port 202 and the fifth refrigerant port 203) through the second on-off valve 22, and enters the enthalpy-increasing auxiliary path (i.e., the first throttling device 25, the third refrigerant port 201 and the fifth refrigerant port 203) through the second on-off valve 22, the low-temperature liquid refrigerant is throttled and cooled by the first throttling device 25 in the enthalpy-increasing auxiliary path, and then absorbs heat from the refrigerant in the enthalpy-increasing main path more efficiently in the economizer 20 to become low-temperature gaseous refrigerant, and the low-temperature gaseous refrigerant output from the enthalpy-increasing auxiliary path returns to the enthalpy-increasing port 121 of the compressor 12 through the fifth on-off valve 26.And the low-temperature liquid refrigerant of the enthalpy-increasing main path is reduced in temperature by heat exchange to become low-temperature liquid refrigerant with even lower temperature, and then enters the third throttling device 36 to be throttled and reduced in temperature, to become low-temperature liquid refrigerant with still lower temperature, and then enters the second refrigerant port 172 of the outdoor heat exchanger 17, and the low-temperature liquid refrigerant is evaporated and absorbs heat in the outdoor heat exchanger 17 to become low-temperature gaseous refrigerant, and the low-temperature gaseous refrigerant output by the first refrigerant port 171 of the outdoor heat exchanger 17 returns to the inlet of the compressor 12 through the second valve port 192 and the third valve port 193 of the first reversing valve 19 and the low-pressure gas-liquid separator 14, and reciprocally circulates. The air source heat pump system can realize the effect of floor heating and the like while heating, and improve energy utilization rate.

[0115] It should be noted that the high, medium and low temperatures are only relative descriptions, and the gaseous refrigerant can also refer to a gas-liquid two-phase state or a gaseous state, which is not limited herein.

[0116] By implementing the utility model, the following beneficial effects are achieved:

[0117] The outdoor main machine has the first cavity 111 and the second cavity 112 inside, the outdoor heat exchange module is arranged in the first cavity 111, the compressor 12, the high-pressure gas-liquid separator 13 and the low-pressure gas-liquid separator 14 are arranged in the second cavity 112, and the electric control module 15 is at least partially arranged in the second cavity 112, and in the vertical direction, the high-pressure gas-liquid separator 13 is located between the electric control module 15 and the compressor 12, so that the space inside the main machine is fully utilized, the space layout is more reasonable, the product is miniaturized, and the pipeline connection between the components is facilitated.

[0118] It can be understood that the above embodiments only express some implementation manners of the utility model, the description is more specific and detailed, but it cannot be understood as a limitation on the patent scope of the utility model. It should be noted that, for ordinary skilled persons in the art, the above embodiments or technical features can be freely combined without departing from the concept of the utility model, and a number of modifications and improvements can be made, which all belong to the protection scope of the utility model, that is, the embodiments described in "in some embodiments" can be freely combined with any of the above embodiments. Therefore, any equivalent transformation and modification within the scope of the claims of the utility model should belong to the scope of the claims of the utility model.

Claims

1. An outdoor host characterized by, The outdoor main unit comprises: a shell, which has a first cavity and a second cavity inside the shell, the second cavity being located on one side of the first cavity in the horizontal direction; an outdoor-side heat exchange module, which is arranged in the first cavity; a compressor, a high-pressure gas-liquid separator and a low-pressure gas-liquid separator, which are arranged in the second cavity; and an electric control module, which is arranged at least partially in the second cavity, and in the vertical direction, the high-pressure gas-liquid separator is located between the electric control module and the compressor. The outdoor main unit further comprises:

2. The outdoor host computer of claim 1, wherein, a partition plate, which is arranged inside the shell, and which separates the internal space enclosed by the shell into the first cavity and the second cavity. The electric control module is located above the partition plate, a part of the electric control module is arranged in the second cavity, another part of the electric control module is arranged in the first cavity, and the electric control module is provided with a heat dissipation channel which communicates the first cavity and the second cavity.

3. The outdoor host of claim 2, wherein, The high-pressure gas-liquid separator is arranged on the partition plate.

4. The outdoor host of claim 2, wherein, The compressor and the low-pressure gas-liquid separator are arranged at the bottom of the second cavity.

5. The outdoor host of claim 1, wherein, The outdoor main unit further comprises:

6. The outdoor host of claim 2, wherein, a first reversing valve and an economizer, which are arranged in the second cavity, and a first switch valve and a second switch valve, which are arranged corresponding to the second cavity; one end of the first switch valve is connected to the first reversing valve, and one end of the second switch valve is connected to the economizer; a third switch valve and a fourth switch valve, which are arranged corresponding to the second cavity; one end of the third switch valve is connected to the outlet of the compressor, and one end of the fourth switch valve is connected to the first refrigerant inlet of the high-pressure gas-liquid separator. The economizer is arranged on the partition plate.

7. The outdoor host of claim 6, wherein, The outdoor main unit further comprises:

8. The outdoor host of claim 6, wherein, a fixing plate, which is arranged in the second cavity and connected to the partition plate and the shell, and on which the first switch valve and the second switch valve are arranged and located in the second cavity; the third switch valve and the fourth switch valve are arranged on the shell and located outside the second cavity. The first reversing valve is located at the middle of the second cavity in the vertical direction, and the first switch valve and the second switch valve are located below the first reversing valve; and / or, the third switch valve and the fourth switch valve are located above the first reversing valve.

9. The outdoor host computer of claim 6 or 8, wherein, The outdoor main unit comprises the outdoor main unit according to any one of claims 1-9.

10. An air source heat pump system characterised in that, ​

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