Heat pump system and energy storage equipment

Abstract

The utility model discloses a heat pump system and energy storage equipment. The heat pump system comprises a compressor, a heat exchanger, an economizer, an electronic expansion valve and a fluorine cooling plate which are sequentially connected. The heat pump system further comprises a liquid spraying cooling loop, one end of the liquid spraying cooling loop is connected between the economizer and the heat exchanger, and the other end of the liquid spraying cooling loop is connected with an air return pipeline between the economizer and the compressor. And the liquid spraying cooling loop is configured to enable a refrigerant entering the compressor after passing through the liquid spraying cooling loop and the gas return pipeline to be in a gas-liquid mixed state. According to the heat pump system, the liquid spraying cooling loop is additionally arranged, so that the heat pump system can reduce the exhaust superheat degree, the refrigerant circulation amount can be increased by increasing the refrigerant suction density of the compressor, and therefore the heat pump system has the good low-temperature heating capacity, the use requirement of a user is met, and the heat pump system is safe and reliable.

Description

Technical Field

[0001] The utility model relates to the technical field of energy storage equipment, in particular to a heat pump system and energy storage equipment. Background Art

[0002] At present, conventional energy storage thermal management products include heat pump systems. However, the heat capacity per unit volume of the heat pump system is small, resulting in a small amount of refrigerant circulation, which leads to insufficient low-temperature heating capacity of the heat pump system and cannot meet the user's usage needs. Utility Model Content

[0003] The embodiments of the present utility model provide a heat pump system and an energy storage device to solve at least one of the above-mentioned technical problems.

[0004] The utility model provides a heat pump system. The heat pump system includes a compressor, a heat exchanger, an economizer, an electronic expansion valve and a fluorine cold plate connected in sequence, and the heat pump system also includes:

[0005] A liquid spray cooling circuit, one end of which is connected between the economizer and the heat exchanger, and the other end of which is connected to a return air pipeline between the economizer and the compressor;

[0006] The liquid spray cooling circuit is configured to make the refrigerant entering the compressor after passing through the liquid spray cooling circuit and the return air pipeline be in a gas-liquid mixed state.

[0007] The above-mentioned heat pump system, by adding a liquid spray cooling circuit, can reduce the exhaust superheat of the heat pump system and increase the refrigerant circulation volume by increasing the refrigerant suction density of the compressor, so that the heat pump system has good low-temperature heating capacity, thereby meeting the user's usage needs and being safe and reliable.

[0008] In certain embodiments, the liquid spray cooling circuit includes a solenoid valve and a capillary tube, and the solenoid valve and the capillary tube are sequentially connected along the flow direction of the refrigerant.

[0009] In certain embodiments, the liquid spray cooling circuit is configured to: obtain the ambient temperature of the heat pump system and the exhaust superheat of the compressor, and control the solenoid valve to open the bypass liquid spray when the ambient temperature is less than a temperature threshold and the exhaust superheat is greater than a first exhaust superheat threshold;

[0010] In the case where the exhaust superheat is less than a second exhaust superheat threshold, the solenoid valve is controlled to close the bypass injection, and the first exhaust superheat threshold is greater than the second exhaust superheat threshold.

[0011] In certain embodiments, the heat pump system comprises:

[0012] a first temperature detection device, the first temperature detection device being used to detect the temperature of the outlet end of the compressor;

[0013] a second temperature detection device, the second temperature detection device being used to detect a saturation temperature corresponding to the pressure at the inlet end of the compressor;

[0014] The difference between the detected temperature of the first temperature detection device and the detected temperature of the second temperature detection device is the exhaust gas superheat degree.

[0015] In certain embodiments, the pipe radius of the liquid spray cooling circuit is less than or equal to one half of the radius of the return air pipe.

[0016] In some embodiments, the heat pump system includes a plurality of the fluorine cold plates and a plurality of the electronic expansion valves, and the electronic expansion valves and the fluorine cold plates are connected in a one-to-one correspondence.

[0017] In some embodiments, the electronic expansion valve and the fluorine cold plate are connected in series to form a connecting branch, the number of the connecting branches is multiple and they are arranged in parallel, one end of the connecting branch is connected to the outlet of the compressor, and the other end is connected to the economizer.

[0018] In some embodiments, the heat pump system includes a four-way valve, a first end of the four-way valve is connected to the outlet end of the compressor, a second end of the four-way valve is connected to the fluorine cold plate, a third end of the four-way valve is connected to the economizer, and a fourth end of the four-way valve is connected to the heat exchanger.

[0019] In certain embodiments, the heat pump system includes an electrically heated low-pressure tank, one end of which is connected to the inlet end of the compressor, and the other end of which is connected to the liquid injection cooling circuit and the economizer.

[0020] An embodiment of the utility model provides an energy storage device, and the energy storage device includes the heat pump system described in any of the above embodiments.

[0021] The above energy storage device, by adding a liquid spray cooling circuit, enables the heat pump system to reduce the exhaust superheat and increase the refrigerant circulation volume by increasing the refrigerant suction density of the compressor, so that the heat pump system has good low-temperature heating capacity, thereby meeting the user's usage needs and being safe and reliable.

[0022] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0024] Figure 1 It is a schematic structural diagram of a heat pump system according to an embodiment of the utility model;

[0025] Figure 2 It is a curve diagram of pressure and enthalpy in the liquid spray cooling circuit of the embodiment of the utility model.

[0026] Description of main component reference numerals:

[0027] Heat pump system 100, compressor 10, heat exchanger 12, economizer 14, electronic expansion valve 16, fluorine cold plate 18, liquid spray cooling circuit 20, return air pipeline 22, first temperature detection device 24, second temperature detection device 26, connecting branch 28, four-way valve 30, electric heating low-pressure tank 32, distributor 34, first pressure sensor 36, second pressure sensor 38, outlet port 102, inlet port 104, solenoid valve 202, capillary 204. DETAILED DESCRIPTION

[0028] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0029] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In the description of the present invention, "multiple" means two or more, unless otherwise clearly and specifically defined.

[0030] In the description of the present utility model, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection. It can be a mechanical connection or an electrical connection. It can be directly connected or indirectly connected through an intermediate medium. It can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0031] In the present utility model, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0032] The disclosure herein provides many different embodiments or examples for realizing different structures of the utility model. In order to simplify the disclosure of the utility model, the components and settings of specific examples are described herein. Of course, they are merely examples, and the purpose is not to limit the utility model. In addition, the utility model may repeat reference numbers and / or reference letters in different examples, and such repetition is for the purpose of simplification and clarity, and does not itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the utility model provides various specific examples of processes and materials, but those of ordinary skill in the art may be aware of the application of other processes and / or the use of other materials.

[0033] See also Figure 1 , an embodiment of the utility model provides a heat pump system 100. The heat pump system 100 includes a compressor 10, a heat exchanger 12, an economizer 14, an electronic expansion valve 16 and a fluorine cold plate 18 connected in sequence. The heat pump system 100 also includes a liquid spray cooling circuit 20, one end of the liquid spray cooling circuit 20 is connected between the economizer 14 and the heat exchanger 12, and the other end is connected to the return air pipeline 22 between the economizer 14 and the compressor 10. The liquid spray cooling circuit 20 is configured to make the refrigerant entering the compressor 10 after passing through the liquid spray cooling circuit 20 and the return air pipeline 22 in a gas-liquid mixed state.

[0034] The above-mentioned heat pump system 100, by adding a liquid spray cooling circuit 20, can reduce the exhaust superheat of the heat pump system 100, and increase the refrigerant circulation volume by increasing the refrigerant suction density of the compressor 10, so that the heat pump system 100 has good low-temperature heating capacity, thereby meeting the user's usage needs and being safe and reliable.

[0035] Specifically, in one embodiment, in a low-temperature environment, the low pressure of the heat pump system 100 is very low, so that the return air density of the compressor 10 is small, and the refrigerant located on the low-pressure side of the outdoor unit (for example, the heat exchanger 12 can be an outdoor unit) is not easy to flow back into the compressor 10 due to the low pressure, so that the supply of refrigerant for circulating flow is small, and thus the heating capacity of the heat pump system 100 is insufficient in a low-temperature environment.

[0036] It can be understood that the utility model adopts a liquid spray cooling method to mix liquid refrigerant into the gaseous refrigerant, so as to spray the gas-liquid mixed refrigerant into the compressor 10 to increase the density of the refrigerant for enthalpy increase, so that the return air density of the compressor 10 increases, and the refrigerant in the compressor 10 realizes the enthalpy increase process, thereby increasing the refrigerant circulation volume, and then improving the heating capacity of the heat pump system 100 under low temperature conditions.

[0037] In one embodiment, if Figure 1 As shown, the fluorine cold plate 18 is equivalent to the indoor unit part of the heat pump system 100, which can be used to adjust the temperature of the battery module so that the battery module can work safely under appropriate temperature conditions. For example, the battery module can be a battery cell, etc., thereby ensuring that the heat pump system 100 provides a suitable heating temperature for the indoor environment.

[0038] In one embodiment, the heat exchanger 12 can be a condenser, that is, the heat exchanger 12 is equivalent to the outdoor unit part, which can evaporate the liquid refrigerant into gaseous refrigerant and re-enter the compressor 10 for compression, so that the refrigerant repeats the work and circulates, so that the heat pump system 100 continuously heats.

[0039] In one embodiment, the economizer 14 can be a two-inlet and two-outlet delivery port. For example, under heating conditions, the refrigerant can enter from the upper left delivery port of the economizer 14, be output from the upper right delivery port, enter from the lower right delivery port, and be output from the lower left delivery port, so that a part of the refrigerant can be formed into a gaseous refrigerant through the heat exchanger 12 and then sucked into the compressor 10, and the other part of the refrigerant (the refrigerant is in a liquid state) is directly delivered to the compressor 10 through the liquid injection cooling circuit 20, without passing through the heat exchanger 12 for the state transformation of the refrigerant, thereby increasing the return air density of the compressor 10, and then increasing the refrigerant supply required for the operation of the compressor 10.

[0040] That is, liquid refrigerant is mixed into the gaseous refrigerant to increase the return air density of the compressor 10, thereby ensuring that the refrigerant in the compressor 10 achieves an enthalpy increase effect, increasing the refrigerant circulation volume, and further improving the heating capacity of the heat pump system 100 under low temperature conditions.

[0041] In one embodiment, if Figure 1 As shown, one end of the liquid spray cooling circuit 20 is connected between the economizer 14 and the heat exchanger 12, and the other end is connected to the return air pipeline 22 between the economizer 14 and the compressor 10, so that the refrigerant in the heat pump system 100 can pass through the liquid spray cooling circuit 20 and the return air pipeline 22 respectively and then be mixed to form a mixed refrigerant, and the mixed refrigerant is then sprayed into the compressor 10 from the inlet end 104 to increase the return air density and enthalpy increase effect in the compressor 10, which is reliable and practical.

[0042] It can be understood that in one example, the liquid refrigerant transported by the liquid spray cooling circuit 20 and the gaseous refrigerant transported by the return air pipeline 22 are mixed before being input to the inlet end 104, so that the mixed refrigerant is cooled and becomes a gas-liquid mixed state, thereby reducing the superheat of the refrigerant at the inlet end 104 of the compressor 10 and increasing the amount of the refrigerant after cooling and liquefaction.

[0043] In addition, compared to the compressor 10 inlet end 104 that only refluxes a single gaseous refrigerant, the compressor 10 inlet end 104 refluxes a refrigerant in a gas-liquid mixed state, which increases the density of the refrigerant, thereby ensuring that the amount of compressible refrigerant in the compressor 10 increases, avoiding insufficient refrigerant return air volume at the compressor 10 inlet end 104 resulting in insufficient heating capacity, thereby increasing the refrigerant circulation volume.

[0044] In one embodiment, if Figure 1 As shown, when the heat pump system 100 is in a heating condition, the refrigerant has two flow paths in the heat pump system 100 .

[0045] For example, in one example, the first refrigerant flow path is: compressor 10-fluorine cold plate 18-electronic expansion valve 16-economizer 14-heat exchanger 12-economizer 14-compressor 10. The second refrigerant flow path is: compressor 10-fluorine cold plate 18-electronic expansion valve 16-economizer 14-liquid spray cooling circuit 20-compressor 10.

[0046] In one embodiment, if Figure 1 As shown, the heat pump system 100 further includes a distributor 34. The distributor 34 is disposed between the economizer 14 and the heat exchanger 12, and is equivalent to a liquid distributor, which can be used to adjust the flow rate of the liquid refrigerant entering the two different branches of the liquid spray cooling circuit 20 and the heat exchanger 12, thereby ensuring that the return air density returning to the compressor 10 is increased, thereby improving the heating capacity of the heat pump system 100 under low temperature conditions, and ensuring the safe operation of the heat pump system 100.

[0047] See also Figure 1 In some embodiments, the liquid spray cooling circuit 20 includes a solenoid valve 202 and a capillary tube 204, and the solenoid valve 202 and the capillary tube 204 are connected in sequence along the flow direction of the refrigerant.

[0048] In this way, the liquid spray cooling circuit 20 can realize controllable opening or closing of the branch, which is flexible and practical.

[0049] Specifically, in one embodiment, the solenoid valve 202 is connected to the liquid spray cooling circuit 20, and can be used to control the liquid refrigerant to flow through the liquid spray cooling circuit 20 in a timely manner. When the heat pump system 100 is in a low temperature environment, it can ensure that the compressor 10 has a higher return air density and refrigerant supply, thereby ensuring that the heat pump system 100 can heat normally and continuously.

[0050] It can be understood that the heat pump system 100 is provided with a solenoid valve 202 in the liquid spray cooling circuit 20, and a distributor 34 is provided between the economizer 14 and the heat exchanger 12. When the heat exchanger 12 is affected by the outdoor low temperature or low pressure and the refrigerant in the heat exchanger 12 cannot flow back to the compressor 10 normally, the reflux loss of the refrigerant can be reduced by reducing the opening of the distributor 34, and at the same time, the solenoid valve 202 is opened to allow the compressor 10 to have a higher return air density and refrigerant supply, thereby ensuring that the heat pump system 100 can continue to heat normally.

[0051] In one embodiment, the heat pump system 100 has a throttling effect by providing a capillary tube 204 in the liquid spray cooling circuit 20. For example, the capillary tube 204 can reduce the reflux of the gaseous refrigerant transported through the heat exchanger 12 to the liquid spray cooling circuit 20, so as to improve the reliability of the liquid spray enthalpy increase, thereby ensuring the safe operation of the compressor 10 and the heat pump system 100 and having good practicality.

[0052] In one embodiment, the heat pump system 100 has a pressure reducing and speed increasing effect by providing a capillary tube 204 in the liquid spray cooling circuit 20. For example, the diameter of the capillary tube 204 is small, so that the flow rate of the liquid refrigerant flowing through the capillary tube 204 is increased and the pressure is reduced, so that the temperature of the liquid refrigerant is relatively low, thereby ensuring that the density of the refrigerant returning to the compressor 10 is relatively large, the refrigerant circulation volume is high, and the heating effect is good.

[0053] In certain embodiments, the liquid spray cooling circuit 20 is configured to: obtain the ambient temperature of the heat pump system 100 and the exhaust superheat of the compressor 10, and control the solenoid valve 202 to open the bypass liquid spray when the ambient temperature is less than the temperature threshold and the exhaust superheat is greater than the first exhaust superheat threshold;

[0054] When the exhaust superheat is less than the second exhaust superheat threshold, the solenoid valve 202 is controlled to close the bypass injection, and the first exhaust superheat threshold is greater than the second exhaust superheat threshold.

[0055] In this way, the heat pump system 100 can continue to heat under low temperature conditions and has good safety.

[0056] Specifically, in one embodiment, the heat pump system 100 may be provided with a processor (not shown) and a temperature sensor (not shown), and the processor is electrically connected to the temperature sensor and the solenoid valve 202 to obtain the ambient temperature of the heat pump system 100 and the exhaust superheat of the compressor 10, and control the opening and closing of the solenoid valve 202 according to the ambient temperature and the exhaust superheat, which is safe and practical.

[0057] In one embodiment, when the ambient temperature is lower than the temperature threshold and the exhaust superheat is greater than the first exhaust superheat threshold, the solenoid valve 202 is controlled to open the bypass liquid spray. This can be understood as follows: the current ambient temperature is particularly low, so that the heat pump system 100 is in an ultra-low temperature environment, making it difficult for the refrigerant on the low-pressure side of the heat pump system 100 to flow back into the compressor 10. At the same time, the refrigerant temperature difference between the outlet end 102 of the compressor 10 and the inlet end 104 of the compressor 10 is greater than the first exhaust superheat threshold, resulting in a small amount of refrigerant circulation or a small amount of refrigerant supply required to be compressed in the compressor 10. At this time, the solenoid valve 202 needs to be opened for bypass liquid spray, and liquid refrigerant is provided through the liquid spray cooling circuit 20 to reduce the temperature and cool the gaseous refrigerant, thereby increasing the return air density at the inlet end 104 of the compressor 10 and the amount of refrigerant supply required to be compressed, thereby ensuring that the refrigerant circulation amount and the heat pump system 100 have good heating capacity and good safety under low temperature conditions.

[0058] It can be understood that the solenoid valve 202 opens the bypass liquid spray, so that the liquid refrigerant transported by the liquid spray cooling circuit 20 is used for cooling and mixing with the gaseous refrigerant transported by the return air pipeline 22, so as to ensure that the density of the mixed refrigerant increases, and the amount of refrigerant returning to the inlet end 104 of the compressor 10 increases, to achieve the enthalpy increase effect, thereby ensuring the normal operation of the compressor 10, and further ensuring that the heat pump system 100 has the ability to continuously heat under low temperature conditions.

[0059] In one embodiment, when the exhaust superheat is less than the second exhaust superheat threshold, the solenoid valve 202 is controlled to close the bypass liquid spray. It can be understood that: at this time, the refrigerant temperature difference between the outlet end 102 of the compressor 10 and the inlet end 104 of the compressor 10 is in an appropriate temperature operating range, and there is no need to cool down the liquid refrigerant transported by the liquid spray cooling circuit 20. The bypass liquid spray is closed by controlling the solenoid valve 202 to ensure the safe service life of the compressor 10 and the normal refrigerant circulation volume, thereby improving the reliability of the heat pump system 100 and improving safety.

[0060] In one embodiment, the temperature threshold may be -10°C or other values, as long as the heat pump system 100 is ensured to work normally, and no specific limitation is made herein.

[0061] In one embodiment, the first exhaust superheat threshold may be 30°C, and the second exhaust superheat threshold may be 15°C. Of course, the first exhaust superheat threshold and the second exhaust superheat threshold may also be other values, as long as the heat pump system 100 works normally, and no specific restrictions are made here.

[0062] That is, in one example, when the ambient temperature is less than -10°C and the exhaust superheat is greater than 30°C, the solenoid valve 202 is controlled to open the bypass liquid injection. When the exhaust superheat is less than 15°C, the solenoid valve 202 is controlled to close the bypass liquid injection to ensure that the refrigerant circulation volume is increased while reducing the exhaust superheat of the compressor 10, thereby improving the heating capacity of the heat pump system 100.

[0063] It is worth noting that, when the exhaust superheat is less than or equal to the first exhaust superheat threshold and greater than or equal to the second exhaust superheat threshold, it means that the current exhaust superheat is within a reasonable range, the solenoid valve 202 maintains the current working state, and the distributor 34 also maintains the current working state, so that the current refrigerant circulation volume of the heat pump system 100 matches the ambient temperature and the exhaust superheat, that is, the current performance and energy efficiency of the heat pump system 100 are adapted to ensure a good effect of liquid injection enthalpy increase, so that the heat pump system 100 maintains a good heating capacity.

[0064] See also Figure 1 In certain embodiments, the heat pump system 100 includes:

[0065] A first temperature detection device 24, the first temperature detection device 24 is used to detect the temperature of the outlet end 102 of the compressor 10;

[0066] A second temperature detection device 26, the second temperature detection device 26 is used to detect the saturation temperature corresponding to the pressure at the inlet end 104 of the compressor 10;

[0067] The difference between the temperature detected by the first temperature detection device 24 and the temperature detected by the second temperature detection device 26 is the exhaust gas superheat degree.

[0068] In this way, the exhaust gas superheat of the compressor 10 is obtained, thereby ensuring the refrigerant circulation amount, which is safe and practical.

[0069] Specifically, in one embodiment, the first temperature detection device 24 can be a temperature sensor or other temperature detection device, which can be used to detect the temperature value of the outlet end 102 of the compressor 10 in real time to ensure that the exhaust superheat is within an appropriate temperature operating range, thereby ensuring the safe operation of the compressor 10 and the heat pump system 100.

[0070] For example, in one example, the first temperature detection device 24 can be set at the outlet end 102 of the compressor 10, or can be set at other positions that meet the temperature detection requirements, and the first temperature detection device 24 is electrically connected to a processor (not shown), so that the processor can control the opening or closing of the solenoid valve 202 by obtaining the exhaust superheat, thereby ensuring the refrigerant circulation amount, and further ensuring the safe operation of the compressor 10 and the heat pump system 100.

[0071] In one embodiment, the second temperature detection device 26 can be a temperature sensor or other temperature detection device, which can be used to detect the temperature value of the inlet end 104 of the compressor 10 in real time to ensure that the exhaust superheat is within an appropriate temperature operating range, thereby ensuring the safe operation of the compressor 10 and the heat pump system 100.

[0072] For example, in one example, the second temperature detection device 26 can be set at the inlet end 104 of the compressor 10, or can be set at other positions that meet the temperature detection requirements, and the second temperature detection device 26 is electrically connected to a processor (not shown), so that the processor can control the opening or closing of the solenoid valve 202 by obtaining the exhaust superheat, thereby ensuring the refrigerant circulation amount, and further ensuring the safe operation of the compressor 10 and the heat pump system 100.

[0073] The difference between the temperature detected by the first temperature detection device 24 and the temperature detected by the second temperature detection device 26 is the exhaust gas superheat degree.

[0074] It is worth noting that if Figure 1 As shown, the inlet end 104 of the compressor 10 may also be provided with a first pressure sensor 36, which can be used to detect the pressure value of the inlet end 104 of the compressor 10, so that the second temperature detection device 26 determines the saturation temperature corresponding to the pressure of the inlet end 104 of the compressor 10 according to the detection result of the first pressure sensor 36, and then obtains the accurate exhaust superheat.

[0075] Of course, the outlet end 102 of the compressor 10 may also be provided with a second pressure sensor 38, which can be used to detect the pressure value of the outlet end 102 of the compressor 10 to ensure that the refrigerant in the heat pump system 100 circulates and heats under appropriate pressure conditions with good safety.

[0076] See also Figure 1In some embodiments, the pipe radius of the liquid spray cooling circuit 20 is less than or equal to half of the radius of the return air pipe 22 .

[0077] In this way, the risk of liquid return is reduced, and the refrigerant can flow back into the compressor 10 normally, which improves safety.

[0078] Specifically, in one embodiment, a suitable pipe radius should be selected for the liquid spray cooling circuit 20 to ensure that the liquid refrigerant safely and quickly passes through the liquid spray cooling circuit 20 into the compressor 10, and to prevent the gaseous refrigerant in the return air pipeline 22 from flowing back into the liquid spray cooling circuit 20 to reduce the refrigerant circulation volume, thereby reducing the risk of liquid return and improving the safety of the operation of the heat pump system 1000.

[0079] In one embodiment, the pipe radius of the liquid spray cooling circuit 20 is less than or equal to half the radius of the return air pipe 22, so that the pipe radius of the liquid spray cooling circuit 20 is smaller, the flow rate of the liquid refrigerant is larger, and reverse reflux is not easy to occur.

[0080] When the pipe radius of the liquid spray cooling circuit 20 is larger than half of the radius of the return air pipeline 22, the pipe radius of the liquid spray cooling circuit 20 and the radius of the return air pipeline 22 become close, which makes it easy for the gaseous refrigerant in the return air pipeline 22 to rush into the liquid spray cooling circuit 20, resulting in a higher risk of liquid return and poor safety.

[0081] The lower limit of the pipe radius of the liquid spray cooling circuit 20 is determined based on experience. It only needs to ensure that the pipe radius of the liquid spray cooling circuit 20 is less than or equal to half of the radius of the return air pipe 22. No specific restrictions are made here.

[0082] For instance, in one example, assuming that the radius of the return air pipe 22 is R, the pipe radius of the liquid spray cooling circuit 20 should be less than or equal to 0.5R, that is, the pipe radius of the liquid spray cooling circuit 20 can be 0.3R, 0.34R, 0.39R, 0.41R, 0.45R, 0.5R or other values ​​less than or equal to 0.5R to ensure that the liquid refrigerant safely and quickly passes through the liquid spray cooling circuit 20 into the compressor 10, and no specific restrictions are made here.

[0083] See also Figure 1 In some embodiments, the heat pump system 100 includes a plurality of fluorine cooling plates 18 and a plurality of electronic expansion valves 16 , and the electronic expansion valves 16 and the fluorine cooling plates 18 are connected in a one-to-one correspondence.

[0084] In this way, the flow rate regulation effect of the electronic expansion valve 16 is improved, thereby ensuring that the refrigerant circulates better.

[0085] Specifically, in one embodiment, the electronic expansion valve 16 and the fluorine cold plate 18 are connected one-to-one, and can be used to adjust the flow rate of the refrigerant flowing through the fluorine cold plate 18, thereby controlling the heating capacity of the fluorine cold plate 18, and then enabling the heat pump system 100 to provide a suitable temperature for the room to ensure a normal production working environment.

[0086] It can be understood that, in one example, the electronic expansion valve 16 can be a shut-off valve, which can be used to adjust the flow rate of the refrigerant to ensure the circulation volume of the refrigerant, thereby meeting the heating capacity requirements of the heat pump system 100 and having good practicality.

[0087] See also Figure 1 In some embodiments, the electronic expansion valve 16 and the fluorine cold plate 18 are connected in series to form a connecting branch 28. The number of connecting branches 28 is multiple and they are arranged in parallel. One end of the connecting branch 28 is connected to the outlet end 102 of the compressor 10, and the other end is connected to the economizer 14.

[0088] In this way, the heating efficiency of the heat pump system 100 is improved, thereby meeting the user's usage needs.

[0089] Specifically, in one embodiment, one end of the connecting branch 28 is connected to the outlet end 102 of the compressor 10, and the other end is connected to the economizer 14, so as to ensure that the refrigerant at the outlet end 102 of the compressor 10 absorbs cold energy in different connecting branches 28 and then is collected into the economizer 14, thereby ensuring that the amount of refrigerant flowing into and out of the connecting branch 28 remains unchanged, thereby ensuring that the heat pump system 100 has the ability of continuous circulation heating.

[0090] In one embodiment, the number of connecting branches 28 is multiple and they are arranged in parallel, so that multiple fluorine cooling plates 18 can heat the same room, thereby quickly increasing the indoor temperature, which is efficient and practical.

[0091] In one embodiment, the number of connecting branches 28 is multiple and they are arranged in parallel, so that the multiple fluorine cooling plates 18 can also heat different rooms respectively, thereby increasing the temperature in multiple rooms at the same time, and the heating efficiency is high.

[0092] See also Figure 1 In some embodiments, the heat pump system 100 includes a four-way valve 30, a first end D of the four-way valve 30 is connected to the outlet end 102 of the compressor 10, a second end E of the four-way valve 30 is connected to the fluorine cold plate 18, a third end S of the four-way valve 30 is connected to the economizer 14, and a fourth end C of the four-way valve 30 is connected to the heat exchanger 12.

[0093] In this way, it is ensured that the heat pump system 100 can realize the refrigerant circulation heating process with good safety.

[0094] Specifically, in one embodiment, Figure 1As shown, when the heat pump system 100 is in a heating state, the first end D and the second end E of the four-way valve 30 are connected, and the third end S and the fourth end C of the four-way valve 30 are connected to ensure that the refrigerant compressed by the compressor 10 can circulate in the heat pump system 100, thereby ensuring that the heat pump system 100 achieves a continuous heating process.

[0095] It is understandable that Figure 1 As shown, during the heating process, there are two flow paths of the refrigerant in the heat pump system 100. The first refrigerant flow path can be: compressor 10-outlet end 102-first temperature detection device 24-first end D of the four-way valve 30-second end E of the four-way valve 30-fluorine cold plate 18-electronic expansion valve 16-economizer 14-distributor 34-heat exchanger 12-fourth end C of the four-way valve 30-third end S of the four-way valve 30-economizer 14-electrically heated low-pressure tank 32-second temperature detection device 26-inlet end 104-compressor 10.

[0096] The second refrigerant flow path can be: compressor 10-outlet end 102-first temperature detection device 24-first end D of four-way valve 30-second end E of four-way valve 30-fluorine cold plate 18-electronic expansion valve 16-economizer 14-solenoid valve 202-capillary tube 204-electrically heated low-pressure tank 32-second temperature detection device 26-inlet end 104-compressor 10.

[0097] In summary, by providing the four-way valve 30 , the refrigerant can circulate smoothly in the heat pump system 100 to generate heat, thereby ensuring the safe operation of the heat pump system 100 .

[0098] Please combine Figure 2 , Figure 2 It is a curve diagram of pressure and enthalpy value in the liquid spray cooling circuit 20 of the present invention.

[0099] in, Figure 2 The meanings of the numbers in the table are as follows: number 1' represents the inlet end 104 of the compressor 10, number 1 represents the outlet end 102 of the compressor 10 (such as Figure 1 ), numeral 2 represents the output end of the fluorine cold plate 18 (the output end of the fluorine cold plate 18 is located at Figure 1 The left end of the fluorine cold plate 18), the number 3 represents the first output end of the economizer 14 (the first output end of the economizer 14 is located at Figure 1 The number 4 indicates the output end of the heat exchanger 12 (the output end of the heat exchanger 12 is located at the upper right end of the economizer 14). Figure 1 The upper end of the heat exchanger 12), the number 5 represents the output end of the capillary 204 (the output end of the capillary 204 is located at Figure 1 The left end of the capillary tube 204 in the middle), the number 6 represents the second output end of the economizer 14 (the second output end of the economizer 14 is located at Figure 1The lower left end of the economizer 14), the number 7 represents the input end of the electric heating low pressure tank 32 (the input end of the electric heating low pressure tank 32 is located at Figure 1 The lower end of the low-pressure tank 32 is heated by the medium power).

[0100] Depend on Figure 2 It can be seen from the curve diagram of pressure and enthalpy value shown that the heat pump heating system in the related art without a liquid spray cooling circuit is an ordinary heating system. The flow direction of the refrigerant in the ordinary heating system during the heating cycle is: 1-2-3-4-6-1'-1, wherein 1 and 1' represent the outlet and inlet ends of the compressor, respectively, that is, the refrigerant in the heat pump heating system in the related art circulates through the outlet end 1 of the compressor, the output end 2 of the fluorine cold plate, the first output end 3 of the economizer, the output end 4 of the heat exchanger, the second output end 6 of the economizer, and the inlet end 1' of the compressor, thereby realizing the circulation of the refrigerant in the heat pump heating system.

[0101] The heat pump system 100 of the utility model adds a liquid spray cooling circuit 20, that is, a part of the refrigerant in the heat pump system 100 flows along the original path 1-2-3-4-6-1'-1, and the other part of the refrigerant flows along the liquid spray cooling circuit 20 (1-2-5-7-1'-1), and converges through the input end 7 of the electric heating low-pressure tank 32 to flow to the inlet end 1' of the compressor 10, thereby increasing the return air density of the compressor 10, that is, the refrigerant is converted from the gaseous refrigerant in the related technology to the refrigerant in the gas-liquid two-phase state and flows into the inlet end 104 of the compressor 10, so that the density of the mixed refrigerant is increased, thereby increasing the refrigerant circulation volume, and then ensuring the heating capacity of the heat pump system 100 under low temperature conditions.

[0102] It can be understood that the liquid spray cooling circuit 20 of the utility model is a gas-liquid two-phase refrigerant with a higher density from the output end 2 of the fluorine cold plate to the output end 5 of the capillary 204, which is mixed with the low-density and low-pressure gaseous refrigerant in the return air pipeline 22 from the output end 4 of the heat exchanger 12 to the second output end 6 of the economizer 14 to the input end 7 of the electric heating low-pressure tank 32 and then enters the compressor 10, thereby reducing the inlet superheat of the compressor 10, increasing the suction density of the compressor 10, and thus increasing the refrigerant circulation volume.

[0103] In summary, if Figure 2 As shown, the heating capacity formula of the heat pump heating system in the related art is Q 6-4 +W 1’-6 The heating capacity of the heat pump system 100 of the present invention is composed of (Q 7-5 +W 1-7 )+(Q 6-4 +W 1’-6 The refrigerant circulation amount of the heat pump system 100 is increased, which means that the heat recovery amount of the liquid spray cooling circuit 20 is increased.

[0104] See also Figure 1 In some embodiments, the heat pump system 100 includes an electrically heated low-pressure tank 32 , one end of which is connected to the inlet end 104 of the compressor 10 , and the other end of which is connected to the liquid injection cooling circuit 20 and the economizer 14 .

[0105] In this way, the normal operation of the compressor 10 is ensured, and the practicality is good.

[0106] Specifically, in one embodiment, the electrically heated low-pressure tank 32 is disposed between the economizer 14 and the inlet end 104 of the compressor 10, and can be used to filter out impurities in the refrigerant, and can increase the temperature of the refrigerant by electrically heating to address the problem that the refrigerant is not easy to flow back to the inlet end 104 of the compressor 10 in an ultra-low temperature environment, thereby ensuring the refrigerant supply to the compressor 10, and further ensuring that the heat pump system 100 has a circulating heating capability.

[0107] In one embodiment, if Figure 1 As shown, the electrically heated low-pressure tank 32 may be located between the capillary tube 204 and the economizer 14, or may be disposed at other positions between the economizer 14 and the inlet end 104 of the compressor 10, to ensure that the refrigerant flows smoothly back to the inlet end 104 of the compressor 10, thereby ensuring the refrigerant circulation amount and ensuring the normal operation of the compressor 10, and no specific limitation is made herein.

[0108] It is worth noting that the electric heating low-pressure tank 32 and the solenoid valve 202 cannot be opened at the same time. For example, when the temperature of the gaseous refrigerant is high and the exhaust superheat is greater than the first exhaust superheat threshold, the solenoid valve 202 needs to be opened to allow the liquid spray cooling circuit 20 to spray liquid refrigerant to cool the gaseous refrigerant. Therefore, the electric heating low-pressure tank 32 cannot be opened to heat the gaseous refrigerant, which will further increase the exhaust superheat and save energy. When the temperature of the gaseous refrigerant is low and the gaseous refrigerant is not easy to flow back to the compressor 10, the electric heating low-pressure tank 32 needs to be opened to appropriately heat and heat the gaseous refrigerant to ensure that the molecular motion is accelerated to alleviate the current situation that the gaseous refrigerant is not easy to flow back to the compressor 10. Therefore, the solenoid valve 202 does not need to be opened to cool the gaseous refrigerant.

[0109] In summary, by providing an electrically heated low-pressure tank 32 to ensure the refrigerant circulation volume in the heat pump system 100, the normal operation of the compressor 10 is ensured, thereby significantly improving the heating capacity of the heat pump system 100 under low temperature conditions, and having good practicality.

[0110] In one example, the electrically heated low-pressure tank 32 may also be a gas-liquid separator, or other devices, as long as the normal operation of the compressor 10 is ensured, and no specific limitation is made here.

[0111] An embodiment of the present utility model provides an energy storage device (not shown), and the energy storage device includes a heat pump system 100 of any of the above embodiments.

[0112] The above-mentioned energy storage device, by adding a liquid spray cooling circuit 20, enables the heat pump system 100 to reduce the exhaust superheat and increase the refrigerant circulation volume by increasing the refrigerant suction density of the compressor 10, so that the heat pump system 100 has good low-temperature heating capacity, thereby meeting the user's usage needs and being safe and reliable.

[0113] Specifically, in one embodiment, the energy storage device includes but is not limited to heat pumps, air conditioners, etc. The energy storage device may also include a battery module, which is used to store electrical energy.

[0114] It should be noted that the above explanations of the implementation and beneficial effects of the heat pump system 100 are also applicable to the energy storage device used in the implementation of the utility model, and will not be repeated here to avoid redundancy.

[0115] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiments or examples are included in at least one embodiment or example of the utility model. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0116] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A heat pump system, characterized in that: The heat pump system comprises a compressor, a heat exchanger, an economizer, an electronic expansion valve and a fluorine cold plate connected in sequence, and the heat pump system also comprises: A liquid spray cooling circuit, one end of which is connected between the economizer and the heat exchanger, and the other end of which is connected to a return air pipeline between the economizer and the compressor; The liquid spray cooling circuit is configured to make the refrigerant entering the compressor after passing through the liquid spray cooling circuit and the return air pipeline be in a gas-liquid mixed state.

2. The heat pump system according to claim 1, characterized in that: The liquid spray cooling circuit includes a solenoid valve and a capillary tube, and the solenoid valve and the capillary tube are connected in sequence along the flow direction of the refrigerant.

3. The heat pump system according to claim 2, characterized in that: The liquid spray cooling circuit is configured to: obtain the ambient temperature of the heat pump system and the exhaust superheat of the compressor, and control the solenoid valve to open the bypass liquid spray when the ambient temperature is less than the temperature threshold and the exhaust superheat is greater than the first exhaust superheat threshold; In the case where the exhaust superheat is less than a second exhaust superheat threshold, the solenoid valve is controlled to close the bypass injection, and the first exhaust superheat threshold is greater than the second exhaust superheat threshold.

4. The heat pump system according to claim 3, characterized in that: The heat pump system comprises: a first temperature detection device, the first temperature detection device being used to detect the temperature of the outlet end of the compressor; a second temperature detection device, the second temperature detection device being used to detect a saturation temperature corresponding to the pressure at the inlet end of the compressor; The difference between the detected temperature of the first temperature detection device and the detected temperature of the second temperature detection device is the exhaust gas superheat degree.

5. The heat pump system according to claim 1, characterized in that: The pipeline radius of the liquid spray cooling circuit is less than or equal to half of the radius of the return air pipeline.

6. The heat pump system according to claim 1, characterized in that: The heat pump system comprises a plurality of the fluorine cold plates and a plurality of the electronic expansion valves, and the electronic expansion valves and the fluorine cold plates are connected in a one-to-one correspondence.

7. The heat pump system according to claim 6, characterized in that: The electronic expansion valve and the fluorine cold plate are connected in series to form a connecting branch. There are multiple connecting branches which are arranged in parallel. One end of the connecting branch is connected to the outlet of the compressor, and the other end is connected to the economizer.

8. The heat pump system according to claim 1, characterized in that: The heat pump system includes a four-way valve, a first end of the four-way valve is connected to the outlet end of the compressor, a second end of the four-way valve is connected to the fluorine cold plate, a third end of the four-way valve is connected to the economizer, and a fourth end of the four-way valve is connected to the heat exchanger.

9. The heat pump system according to claim 1, characterized in that: The heat pump system comprises an electrically heated low-pressure tank, one end of which is connected to the inlet end of the compressor, and the other end of which is connected to the liquid spray cooling circuit and the economizer.

10. An energy storage device, characterized in that: A heat pump system comprising any one of claims 1 to 9.

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