Water source high-temperature heat pump system

Abstract

The invention discloses a water source high-temperature heat pump system. The water source high-temperature heat pump system comprises a compressor, a condenser, a heat regenerator, a first ejector, a first flash tank and an evaporator. An exhaust port of the compressor is connected with an inlet of the condenser; an outlet of the condenser is connected with a liquid channel inlet of the heat regenerator, and a liquid channel outlet of the heat regenerator is connected with a driving fluid inlet of the first ejector; an outlet of the first ejector is connected with an inlet of the first flash-tank, a liquid outlet of the first flash-tank is connected with an inlet of the evaporator, and an outlet of the evaporator is connected with an ejected fluid inlet of the first ejector; a gas outlet of the first flash tank is connected with a gas channel inlet of the heat regenerator, and a gas channel outlet of the heat regenerator is connected with a gas suction port of the compressor. By adopting the scheme, the problems of high power consumption and poor system economy are solved.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pumps, and in particular to a water source high-temperature heat pump system. Background Art

[0002] Existing high-temperature heat pump systems mostly use a single-stage compression cycle or a quasi-two-stage compression cycle, including a compressor, a condenser, an expansion valve, an evaporator, an economizer, etc.

[0003] However, the existing high-temperature heat pump system has a large high-to-low pressure ratio, a high exhaust temperature, and high power consumption. Especially when the temperature is high, the system economy is relatively poor. Summary of the invention

[0004] The present invention provides a water source high temperature heat pump system to solve the problems of high power consumption and poor system economy.

[0005] According to one aspect of the present invention, a water source high temperature heat pump system is provided, the water source high temperature heat pump system comprising a compressor, a condenser, a regenerator, a first ejector, a first flasher, and an evaporator;

[0006] The exhaust port of the compressor is connected to the inlet of the condenser;

[0007] The outlet of the condenser is connected to the inlet of the liquid channel of the regenerator, and the outlet of the liquid channel of the regenerator is connected to the ejection fluid inlet of the first ejector;

[0008] The outlet of the first ejector is connected to the inlet of the first flasher, the liquid outlet of the first flasher is connected to the inlet of the evaporator, and the outlet of the evaporator is connected to the ejected fluid inlet of the first ejector;

[0009] The gas outlet of the first flasher is connected to the gas channel inlet of the regenerator, and the gas channel outlet of the regenerator is connected to the air intake of the compressor.

[0010] In an optional embodiment of the present invention, it further comprises a first temperature detecting member, a first pressure detecting member and a first regulating valve, wherein the first temperature detecting member and the first pressure detecting member are arranged on a pipeline between the outlet of the evaporator and the ejected fluid inlet of the first ejector;

[0011] The first regulating valve is disposed on a pipeline between a liquid outlet of the first flash evaporator and an inlet of the evaporator.

[0012] In an optional embodiment of the present invention, a control module is further included, wherein a first input end of the control module is electrically connected to the first temperature detection element, a second input end of the control module is electrically connected to the first pressure detection element, and a first output end of the control module is electrically connected to the first regulating valve;

[0013] The control module is used to: obtain the actual fluid temperature detected by the first temperature detection component, obtain the actual fluid pressure detected by the first pressure detection component, determine the fluid saturation temperature based on the actual fluid pressure, and adjust the opening of the first regulating valve based on the actual fluid temperature and the fluid saturation temperature.

[0014] In an optional embodiment of the present invention, it also includes an oil separator, a second ejector, a second flasher, and an oil cooler;

[0015] The oil separator is connected between the compressor and the condenser, and the refrigerant inlet of the oil separator is connected to the exhaust port of the compressor, and the refrigerant outlet of the oil separator is connected to the inlet of the condenser;

[0016] The oil outlet of the oil separator is connected to the oil channel inlet of the oil cooler, and the oil channel outlet of the oil cooler is connected to the oil return port of the compressor;

[0017] The ejection fluid inlet of the second ejector is connected to the liquid channel outlet of the regenerator, the outlet of the second ejector is connected to the inlet of the second flasher, the liquid outlet of the second flasher is connected to the refrigerant channel inlet of the oil cooler, and the refrigerant channel outlet of the oil cooler is connected to the ejected fluid inlet of the second ejector;

[0018] The gas outlet of the second flasher is connected to the gas supply port of the compressor.

[0019] In an optional embodiment of the present invention, it further comprises a second temperature detection member and a second regulating valve, wherein the second temperature detection member is arranged on a pipeline between the oil channel outlet of the oil cooler and the oil return port of the compressor;

[0020] The second regulating valve is disposed on a pipeline between a liquid outlet of the second flasher and an inlet of a refrigerant passage of the oil cooler.

[0021] In an optional embodiment of the present invention, the third input end of the control module is electrically connected to the second temperature detection element, and the second output end of the control module is electrically connected to the second regulating valve;

[0022] The control module is specifically used to: obtain the measured oil supply temperature detected by the second temperature detection component, and adjust the opening of the second regulating valve based on the measured oil supply temperature and a preset oil supply temperature.

[0023] In an optional embodiment of the present invention, the preset fuel supply temperature includes a preset maximum fuel supply temperature and a preset minimum fuel supply temperature, and the control module is specifically used to:

[0024] When the measured oil supply temperature is greater than or equal to the preset minimum oil supply temperature and less than or equal to the preset maximum oil supply temperature, the opening of the second regulating valve remains unchanged;

[0025] When the measured oil supply temperature is greater than the preset maximum oil supply temperature, increasing the opening of the second regulating valve;

[0026] When the measured oil supply temperature is lower than the preset minimum oil supply temperature, the opening of the second regulating valve is reduced.

[0027] In an optional embodiment of the present invention, it further includes a second pressure detection member and a third regulating valve, and the second pressure detection member and the third regulating valve are both arranged on the pipeline between the gas outlet of the second flasher and the air supply port of the compressor.

[0028] In an optional embodiment of the present invention, the fourth input end of the control module is electrically connected to the second pressure detection element, and the third output end of the control module is electrically connected to the third regulating valve;

[0029] The control module is used to obtain the measured air supply pressure detected by the second pressure detection component, and adjust the opening of the third regulating valve based on the measured air supply pressure and the target air supply pressure.

[0030] In an optional embodiment of the present invention, the control module is specifically used for:

[0031] When the measured air supply pressure is greater than the target air supply pressure, reducing the opening of the third regulating valve;

[0032] When the measured air supply pressure is less than the target air supply pressure, the opening of the third regulating valve is increased.

[0033] The technical solution of the embodiment of the present invention is to set a first ejector, a first flasher, an evaporator and a regenerator, and the condensed refrigerant is used as the ejection fluid. The refrigerant discharged from the outlet of the ejector evaporator is ejected. After the mixed fluid passes through the first flasher, the gaseous refrigerant and the liquid refrigerant are separated. The gaseous refrigerant enters the suction port of the compressor after being superheated by the regenerator, thereby increasing the suction pressure of the compressor and reducing the high and low pressure ratio compared with the related technology, thereby reducing the power consumption of the compressor, improving the cycle performance coefficient COP of the water source high temperature heat pump system, improving the economy of the water source high temperature heat pump system, and solving the problems of high power consumption and poor system economy.

[0034] It should be understood that the contents described in this section are not intended to identify the key or important features of the embodiments of the present invention, nor are they intended to limit the scope of the present invention. Other features of the present invention will become easily understood through the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0036] Figure 1 is a schematic structural diagram of a water source high temperature heat pump system provided according to an embodiment of the present invention;

[0037] Figure 2 It is a circuit block diagram of a water source high temperature heat pump system provided according to an embodiment of the present invention.

[0038] Among them: 1. compressor; 2. oil separator; 3. condenser; 4. regenerator; 5. first ejector; 6. first flasher; 7. first regulating valve; 8. evaporator; 9. second ejector; 10. second flasher; 11. second regulating valve; 12. oil cooler; 13. third regulating valve; 14. first pressure detection element; 15. first temperature detection element; 16. second temperature detection element; 17. second pressure detection element; 18. control module. DETAILED DESCRIPTION

[0039] In order to enable those skilled in the art to better understand the scheme of the present invention, the technical scheme in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of the present invention.

[0040] It should be noted that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchanged where appropriate, so that the embodiments of the present invention described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0041] Figure 1 The schematic diagram of the structure of a water source high temperature heat pump system provided by an embodiment of the present invention is a heat pump system that uses a water source to provide heat. The connection in the water source high temperature heat pump system refers to connection through pipes, which will not be described in detail below. Figure 1 As shown, the water source high temperature heat pump system includes a compressor 1, a condenser 3, a regenerator 4, a first ejector 5, a first flasher 6, and an evaporator 8.

[0042] The exhaust port of the compressor 1 is connected to the inlet of the condenser 3; the outlet of the condenser 3 is connected to the inlet of the liquid channel of the regenerator 4. The compressor 1 consumes electric energy to raise the low-temperature and low-pressure refrigerant to high-temperature and high-pressure. The high-temperature and high-pressure refrigerant exchanges heat with the cooling water source through the condenser 3. The heat released by the refrigerant will be absorbed by the water source, and the refrigerant will change from gas to liquid. The liquid refrigerant discharged from the outlet of the condenser 3 will enter the inlet of the liquid channel of the regenerator 4.

[0043] The liquid channel outlet of the regenerator 4 is connected to the ejection fluid inlet of the first ejector 5, the outlet of the first ejector 5 is connected to the inlet of the first flasher 6, the liquid outlet of the first flasher 6 is connected to the inlet of the evaporator 8, and the outlet of the evaporator 8 is connected to the ejected fluid inlet of the first ejector 5. The gas outlet of the first flasher 6 is connected to the gas channel inlet of the regenerator 4, and the gas channel outlet of the regenerator 4 is connected to the suction port of the compressor 1.

[0044] The first ejector 5 is a device that uses a high-speed high-energy flow (liquid flow, air flow or other material flow) to eject another low-speed low-energy flow. The jet flows into the mixing chamber through a contraction-shaped nozzle, and the surrounding is the ejected jet flow. Through the mixing effect of the boundary, the ejected jet transfers energy to the ejected jet flow. The main function of the first flasher 6 is to gasify the other part of the refrigerant into refrigerant vapor by utilizing the heat released by the condensation of a part of the refrigerant into liquid.

[0045] The refrigerant discharged from the liquid channel outlet of the regenerator 4 enters the injection fluid inlet of the first ejector 5 as the injection fluid, and injects the refrigerant discharged from the outlet of the evaporator 8 to the injected fluid inlet of the first ejector 5. Then, the mixed fluid discharged from the outlet of the first ejector 5 passes through the first flash evaporator 6 to separate the gaseous refrigerant and the liquid refrigerant. The liquid refrigerant discharged from the liquid outlet of the first flash evaporator 6 enters the evaporator 8 through the inlet of the evaporator 8 to absorb the heat of the waste hot water and vaporizes. The gaseous refrigerant discharged from the gas outlet of the first flash evaporator 6 enters from the gas channel inlet of the regenerator 4, exchanges heat with the liquid refrigerant in the liquid channel of the regenerator 4, and then is discharged from the gas channel outlet of the regenerator 4 to the suction port of the compressor 1.

[0046] In the above scheme, by setting a first ejector 5, a first flasher 6, an evaporator 8 and a regenerator 4, the condensed refrigerant is used as the ejection fluid, and the refrigerant discharged from the outlet of the ejector evaporator 8 is ejected. After the mixed fluid passes through the first flasher 6, the gaseous refrigerant and the liquid refrigerant are separated. The gaseous refrigerant enters the suction port of the compressor 1 after being superheated by the regenerator 4, thereby increasing the suction pressure of the compressor 1 and reducing the high-low pressure ratio compared with the related technology, thereby reducing the power consumption of the compressor 1, improving the cycle performance coefficient COP of the water source high-temperature heat pump system, improving the economy of the water source high-temperature heat pump system, and solving the problems of high power consumption and poor system economy.

[0047] In an optional embodiment of the present invention, Figure 1 As shown, the water source high temperature heat pump system also includes a first temperature detection component 15, a first pressure detection component 14 and a first regulating valve 7. The first temperature detection component 15 and the first pressure detection component 14 are arranged on the pipeline between the outlet of the evaporator 8 and the inlet of the ejected fluid of the first ejector 5; the first regulating valve 7 is arranged on the pipeline between the liquid outlet of the first flasher 6 and the inlet of the evaporator 8.

[0048] The first temperature detection member 15 refers to a component capable of detecting temperature. Preferably, the first temperature detection member 15 includes a temperature sensor, so that the temperature can be conveniently detected. By arranging the first temperature detection member 15 on the pipeline between the outlet of the evaporator 8 and the ejected fluid inlet of the first ejector 5, the first temperature detection member 15 can detect the temperature of the fluid flowing through the pipeline between the outlet of the evaporator 8 and the ejected fluid inlet of the first ejector 5, that is, the actual fluid temperature.

[0049] The first pressure detection member 14 refers to a component capable of detecting pressure. Preferably, the first pressure detection member 14 includes a pressure sensor or a pressure gauge, so that the pressure can be conveniently detected. By arranging the first pressure detection member 14 on the pipeline between the outlet of the evaporator 8 and the ejected fluid inlet of the first ejector 5, the first pressure detection member 14 can detect the pressure of the fluid flowing through the pipeline between the outlet of the evaporator 8 and the ejected fluid inlet of the first ejector 5, that is, the actual fluid pressure.

[0050] The first regulating valve 7 is a valve that can control the flow rate of refrigerant in the pipeline between the liquid outlet of the first flasher 6 and the inlet of the evaporator 8. When the first regulating valve 7 is opened, the liquid refrigerant discharged from the liquid outlet of the first flasher 6 can enter the inlet of the evaporator 8. When the first regulating valve 7 is closed, the liquid refrigerant discharged from the liquid outlet of the first flasher 6 cannot enter the inlet of the evaporator 8. In addition, the flow rate and pressure of the refrigerant will be different when the opening degree of the first regulating valve 7 is different.

[0051] Preferably, the first regulating valve 7 includes an expansion valve, which mainly controls the flow rate and pressure of the fluid by reducing the flow area to achieve a throttling effect. When the fluid passes through the expansion valve, the valve automatically adjusts the flow channel size according to the control signal to achieve the desired flow rate and pressure. By making the first regulating valve 7 an expansion valve, the liquid refrigerant discharged from the liquid outlet of the first flasher 6 can be throttled before entering the inlet of the evaporator 8, so that the liquid refrigerant reaches the desired flow rate and pressure.

[0052] Based on the above embodiments, Figure 1 and Figure 2 As shown, the water source high temperature heat pump system also includes a control module 18, a first input end of the control module 18 is electrically connected to the first temperature detection component 15, a second input end of the control module 18 is electrically connected to the first pressure detection component 14, and a first output end of the control module 18 is electrically connected to the first regulating valve 7; the control module 18 is used to: obtain the actual fluid temperature detected by the first temperature detection component 15, obtain the actual fluid pressure detected by the first pressure detection component 14, determine the fluid saturation temperature based on the actual fluid pressure, and adjust the opening of the first regulating valve 7 based on the actual fluid temperature and the fluid saturation temperature.

[0053] The control module 18 refers to a functional module for performing logic control. In some embodiments, the control module 18 includes a controller. In some embodiments, the controller is a dedicated heat pump controller. In some embodiments, the control module 18 includes a PLC or an MCU. It is understood that in other embodiments, the control module 18 may also be other modules that can control the first regulating valve 7, which is not specifically limited here, but is only used as an example.

[0054] The fluid saturation temperature is the saturation temperature of the fluid. The saturation temperature refers to the temperature when the number of vaporized molecules and the number of condensed molecules reach a dynamic equilibrium during the evaporation of the liquid. A certain saturation temperature of a substance must correspond to a certain saturation pressure. Therefore, by measuring the actual fluid pressure, the fluid saturation temperature can be obtained according to the actual fluid pressure. In a heat pump system, when the fluid is a refrigerant, the actual fluid temperature is the actual temperature of the refrigerant, and the fluid saturation temperature is the saturation temperature of the refrigerant. The actual temperature of the refrigerant at the outlet of the evaporator 8 needs to maintain a certain difference with the refrigerant saturation temperature, so that the refrigerant flow is appropriate and the refrigerant can be effectively converted into steam, thereby achieving a refrigeration effect. It can be understood that in this embodiment, the actual fluid pressure refers to the refrigerant pressure flowing through the pipeline, which will not be repeated below.

[0055] When the opening of the first regulating valve 7 is different, the flow rate of the refrigerant can be changed. Since the refrigerant entering the evaporator 8 needs to reach a certain flow rate, and the actual refrigerant temperature is the actual temperature of the refrigerant flowing out of the evaporator 8 currently measured, the opening of the first regulating valve 7 is adjusted based on the difference between the actual refrigerant temperature and the refrigerant saturation temperature, the refrigerant flow rate can be changed to improve the effectiveness of the evaporator 8 and achieve a more effective refrigeration effect.

[0056] Exemplarily, the control module 18 is specifically used to: when the difference between the actual refrigerant temperature and the refrigerant saturation temperature is greater than the maximum target value, increase the opening of the first regulating valve 7; when the difference between the actual refrigerant temperature and the refrigerant saturation temperature is less than the minimum target value, decrease the opening of the first regulating valve 7; when the actual refrigerant temperature and the refrigerant saturation temperature are greater than or equal to the minimum target value and less than or equal to the maximum target value, the opening of the first regulating valve 7 remains unchanged.

[0057] Among them, when the difference between the actual refrigerant temperature and the refrigerant saturation temperature is greater than the maximum target value, it means that the refrigerant flow entering the evaporator 8 is too small, so at this time, the opening of the first regulating valve 7 is increased to increase the actual refrigerant flow, thereby ensuring that the evaporator 8 is in a phase change heat transfer state, so that the refrigerant in the evaporator 8 can be more effectively converted into steam, thereby achieving a refrigeration effect.

[0058] When the difference between the actual refrigerant temperature and the refrigerant saturation temperature is less than the minimum target value, it means that the refrigerant flow entering the evaporator 8 is too large, so at this time, the opening of the first regulating valve 7 is reduced to reduce the actual refrigerant flow, so that the area of ​​the evaporator 8 is fully utilized, and the refrigerant in the evaporator 8 can be more effectively converted into steam, thereby achieving a refrigeration effect.

[0059] In an optional embodiment of the present invention, Figure 1As shown, the water source high temperature heat pump system also includes an oil separator 2, a second ejector 9, a second flasher 10, and an oil cooler 12; the oil separator 2 is connected between the compressor 1 and the condenser 3, and the refrigerant inlet of the oil separator 2 is connected to the exhaust port of the compressor 1, and the refrigerant outlet of the oil separator 2 is connected to the inlet of the condenser 3; the oil outlet of the oil separator 2 is connected to the oil channel inlet of the oil cooler 12, and the oil channel outlet of the oil cooler 12 is connected to the oil return port of the compressor 1.

[0060] Among them, the compressor 1 consumes electric energy to raise the low-temperature and low-pressure refrigerant to high-temperature and high-pressure. The high-temperature and high-pressure refrigerant passes through the oil separator 2. At this time, the oil separator 2 separates the lubricating oil in the high-pressure refrigerant discharged from the compressor 1, and discharges the refrigerant to the condenser 3. After the condenser 3 exchanges heat with the cooling water source, the heat released by the refrigerant will be absorbed by the water source, and the refrigerant will change from gas to liquid. The liquid refrigerant discharged from the outlet of the condenser 3 will enter the liquid channel inlet of the regenerator 4. The lubricating oil discharged from the oil separator 2 will enter the oil channel from the oil channel inlet of the oil cooler 12, and then be discharged from the oil channel outlet of the oil cooler 12 to the oil return port of the compressor 1.

[0061] The ejection fluid inlet of the second ejector 9 is connected to the liquid channel outlet of the regenerator 4, the outlet of the second ejector 9 is connected to the inlet of the second flasher 10, the liquid outlet of the second flasher 10 is connected to the refrigerant channel inlet of the oil cooler 12, the refrigerant channel outlet of the oil cooler 12 is connected to the ejected fluid inlet of the second ejector 9; the gas outlet of the second flasher 10 is connected to the air supply port of the compressor 1.

[0062] Among them, the refrigerant discharged from the liquid channel outlet of the regenerator 4 enters the injection fluid inlet of the second ejector 9 as the injection fluid, and injects the refrigerant discharged from the refrigerant channel outlet of the oil cooler 12 to the injected fluid inlet of the second ejector 9. Then, the mixed fluid discharged from the outlet of the second ejector 9 passes through the second flash evaporator 10 to separate the gaseous refrigerant and the liquid refrigerant. The liquid refrigerant discharged from the liquid outlet of the second flash evaporator 10 enters the oil cooler 12 through the refrigerant channel inlet of the oil cooler 12, exchanges heat with the lubricating oil in the oil channel of the oil cooler 12, absorbs the heat of the lubricating oil and vaporizes. The gaseous refrigerant discharged from the gas outlet of the second flash evaporator 10 is discharged to the air supply port of the compressor 1.

[0063] The above scheme can ensure that the oil supply temperature of the compressor 1 is within a limited range by cooling the lubricating oil entering the oil cooler 12 through the refrigerant entering the oil cooler 12. At the same time, the gaseous refrigerant discharged from the gas outlet of the second flash unit 10 is discharged to the air supply port of the compressor 1, and the air supply of the compressor 1 is utilized to further reduce the exhaust temperature of the compressor 1.

[0064] In an optional embodiment of the present invention, the water source high temperature heat pump system also includes a second temperature detection component 16 and a second regulating valve 11. The second temperature detection component 16 is arranged on the pipeline between the oil channel outlet of the oil cooler 12 and the oil return port of the compressor 1; the second regulating valve 11 is arranged on the pipeline between the liquid outlet of the second flasher 10 and the refrigerant channel inlet of the oil cooler 12.

[0065] The second temperature detection member 16 refers to a component capable of detecting temperature. Preferably, the second temperature detection member 16 includes a temperature sensor, so that the temperature can be conveniently detected. By arranging the second temperature detection member 16 on the pipeline between the oil channel outlet of the oil cooler 12 and the oil return port of the compressor 1, the second temperature detection member 16 can detect the temperature of the lubricating oil discharged from the oil channel outlet of the oil cooler 12 to the compressor 1, that is, the oil supply temperature can be measured, and the measured oil supply temperature is the actual measured oil supply temperature.

[0066] The second regulating valve 11 is a valve that can control the refrigerant flow rate between the liquid outlet of the second flasher 10 and the refrigerant channel inlet of the oil cooler 12. When the second regulating valve 11 is opened, the refrigerant discharged from the liquid outlet of the second flasher 10 can enter the refrigerant channel inlet of the oil cooler 12. When the second regulating valve 11 is closed, the refrigerant discharged from the liquid outlet of the second flasher 10 cannot enter the refrigerant channel inlet of the oil cooler 12. In addition, the opening degree of the second regulating valve 11 is different, and the flow rate of the refrigerant entering the oil cooler 12 is different. At this time, the heat exchange effect on the lubricating oil of the oil cooler 12 is different, that is, the temperature of the lubricating oil after passing through the oil cooler 12 will be different.

[0067] Based on the above embodiments, Figure 1 and Figure 2 As shown, the third input end of the control module 18 is electrically connected to the second temperature detection component 16, and the second output end of the control module 18 is electrically connected to the second regulating valve 11; the control module 18 is specifically used to: obtain the measured oil supply temperature detected by the second temperature detection component 16, and adjust the opening of the second regulating valve 11 based on the measured oil supply temperature and the preset oil supply temperature.

[0068] The preset oil supply temperature refers to the oil supply temperature at which the viscosity of the lubricating oil is moderate, which can better lubricate mechanical parts, reduce wear, and extend the service life of the compressor 1. When the types of the compressor 1 and the lubricating oil are different, the preset oil supply temperature may also be different, and the specific value of the preset oil supply temperature is not specifically limited here.

[0069] The measured oil supply temperature is the actual oil supply temperature of the current lubricating oil, and the preset oil supply temperature is the ideal oil supply temperature. When the opening of the second regulating valve 11 is different, the cooling effect on the lubricating oil of the oil cooler 12 is different, and thus the oil supply temperature is different. Therefore, adjusting the opening of the second regulating valve 11 based on the measured oil supply temperature and the preset oil supply temperature can ensure that the measured oil supply temperature is within an appropriate range, which helps to maintain the stable operation of the compressor 1, reduce performance changes and failures caused by excessively high or low oil temperature, and improve the stability of the entire system.

[0070] Exemplarily, the preset fuel supply temperature includes a preset maximum fuel supply temperature and a preset minimum fuel supply temperature. The control module 18 is specifically used to: when the measured fuel supply temperature is greater than or equal to the preset minimum fuel supply temperature and less than or equal to the preset maximum fuel supply temperature, the opening of the second regulating valve 11 remains unchanged; when the measured fuel supply temperature is greater than the preset maximum fuel supply temperature, the opening of the second regulating valve 11 is increased; when the measured fuel supply temperature is less than the preset minimum fuel supply temperature, the opening of the second regulating valve 11 is decreased.

[0071] The preset maximum value of the oil supply temperature refers to the value that the oil supply temperature should not exceed when the temperature of the lubricating oil inside the compressor 1 is kept within a suitable range, and the preset minimum value of the oil supply temperature refers to the value that the oil supply temperature should not be less than when the temperature of the lubricating oil inside the compressor 1 is kept within a suitable range. When the measured oil supply temperature is greater than the preset maximum value of the oil supply temperature, it means that the oil supply temperature is too high. At this time, increasing the opening of the second regulating valve 11 can allow more refrigerant to enter the oil cooler 12, thereby achieving a better cooling effect on the lubricating oil, and reducing the temperature of the lubricating oil discharged from the oil cooler 12 to the compressor 1, that is, the actual oil supply temperature is reduced, so that the measured oil supply temperature can be closer to the preset maximum value of the oil supply temperature, until the measured oil supply temperature is greater than or equal to the preset minimum value of the oil supply temperature and less than or equal to the preset maximum value of the oil supply temperature.

[0072] When the measured oil supply temperature is less than the preset minimum oil supply temperature, it means that the oil supply temperature is too low. At this time, reducing the opening of the second regulating valve 11 can reduce the amount of refrigerant entering the oil cooler 12, so that the temperature of the lubricating oil discharged from the oil cooler 12 to the compressor 1 increases, that is, the actual oil supply temperature increases, so that the measured oil supply temperature can be closer to the preset minimum oil supply temperature, until the measured oil supply temperature is greater than or equal to the preset minimum oil supply temperature and less than or equal to the preset maximum oil supply temperature.

[0073] Through the above scheme, the temperature of the lubricating oil entering the compressor 1 can be effectively controlled so that the measured oil supply temperature is greater than or equal to the preset minimum oil supply temperature and less than or equal to the preset maximum oil supply temperature, that is, the actual oil supply temperature is within an appropriate range, which helps to maintain the stable operation of the compressor 1, reduce performance changes and failures caused by excessively high or low oil temperature, and improve the stability of the entire system.

[0074] In an optional embodiment of the present invention, Figure 1 and Figure 2 As shown, the water source high temperature heat pump system also includes a second pressure detection component 17 and a third regulating valve 13, and the second pressure detection component 17 and the third regulating valve 13 are both arranged on the pipeline between the gas outlet of the second flasher 10 and the air supply port of the compressor 1.

[0075] The second pressure detection component 17 refers to a component capable of detecting pressure. Preferably, the second pressure detection component 17 includes a pressure sensor or a pressure gauge, so that the pressure can be conveniently detected. By arranging the second pressure detection component 17 on the pipeline between the gas outlet of the second flasher 10 and the air supply port of the compressor 1, the second pressure detection component 17 can detect the pressure of the gaseous refrigerant flowing through the pipeline between the gas outlet of the second flasher 10 and the air supply port of the compressor 1, that is, the pressure of the air supply for the compressor 1 can be actually measured, and the obtained pressure value is the measured air supply pressure.

[0076] The third regulating valve 13 is a valve that can control the pipeline resistance between the gas outlet of the second flasher 10 and the gas supply port of the compressor 1. When the third regulating valve 13 is opened, the gaseous refrigerant discharged from the gas outlet of the second flasher 10 can enter the gas supply port of the compressor 1 to supply gas to the compressor 1. When the third regulating valve 13 is closed, the gaseous refrigerant discharged from the gas outlet of the second flasher 10 cannot enter the gas supply port of the compressor 1, that is, it is impossible to supply gas to the compressor 1. In addition, the pressure of the gaseous refrigerant entering the compressor 1 is different when the opening degree of the third regulating valve 13 is different, that is, the gas supply pressure of the compressor 1 is different.

[0077] Based on the above embodiments, Figure 1 and Figure 2 As shown, the fourth input end of the control module 18 is electrically connected to the second pressure detection component 17, and the third output end of the control module 18 is electrically connected to the third regulating valve 13; the control module 18 is used to: obtain the actual air supply pressure detected by the second pressure detection component 17, and adjust the opening of the third regulating valve 13 based on the actual air supply pressure and the target air supply pressure.

[0078] Among them, the target air supply pressure refers to the pressure that the gaseous refrigerant entering the air supply port of the compressor 1 should reach, and the measured air supply pressure is the pressure of the gaseous refrigerant actually entering the air supply port of the compressor 1. By adjusting the opening of the third regulating valve 13 based on the measured air supply pressure and the target air supply pressure, the air supply pressure of the compressor 1 can be controlled. By controlling the air supply pressure, the operating state of the compressor 1 can be optimized, the under-compression process can be reduced, and the increase in the volumetric specific work of the compressor 1 can be reduced, thereby improving the efficiency and stability of the system. At the same time, during the under-compression process, the power consumption of the compressor 1 can be reduced by controlling the air supply pressure, thereby reducing the energy consumption of the entire system. In the water source high-temperature heat pump system, the thermal performance of the system can be optimized by controlling the air supply pressure, the heating energy efficiency ratio can be improved, and the industrial heating needs can be met. Finally, the air supply pressure control enables the system to better adapt to different workloads and water source temperature changes and maintain the normal operation of the system.

[0079] Exemplarily, the control module 18 is specifically used to: when the measured inflated air pressure is greater than the target inflated air pressure, reduce the opening of the third regulating valve 13; when the measured inflated air pressure is less than the target inflated air pressure, increase the opening of the third regulating valve 13. In addition, when the measured inflated air pressure is equal to the target inflated air pressure, keep the opening of the third regulating valve 13 unchanged.

[0080] Among them, when the measured inflatable gas pressure is greater than the target inflatable gas pressure, it means that the actual inflatable gas pressure is too large. At this time, reducing the opening of the third regulating valve 13 can reduce the inflatable gas pressure. When the measured inflatable gas pressure is less than the target inflatable gas pressure, it means that the actual inflatable gas pressure is too small. At this time, increasing the opening of the third regulating valve 13 can increase the inflatable gas pressure. Therefore, by controlling the opening of the third regulating valve 13, the inflatable gas pressure can be adjusted so that the measured inflatable gas pressure is equal to the target inflatable gas pressure, which effectively improves the performance of the system.

[0081] It should be understood that the various forms of processes shown above can be used to reorder, add or delete steps. For example, the steps described in the present invention can be executed in parallel, sequentially or in different orders, as long as the desired results of the technical solution of the present invention can be achieved, and this document does not limit this.

[0082] The above specific implementations do not constitute a limitation on the protection scope of the present invention. It should be understood by those skilled in the art that various modifications, combinations, sub-combinations and substitutions can be made according to design requirements and other factors. Any modification, equivalent substitution and improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A water source high temperature heat pump system, characterized in that: It includes a compressor, a condenser, a regenerator, a first ejector, a first flash unit, and an evaporator; The exhaust port of the compressor is connected to the inlet of the condenser; The outlet of the condenser is connected to the inlet of the liquid channel of the regenerator, and the outlet of the liquid channel of the regenerator is connected to the ejection fluid inlet of the first ejector; The outlet of the first ejector is connected to the inlet of the first flasher, the liquid outlet of the first flasher is connected to the inlet of the evaporator, and the outlet of the evaporator is connected to the ejected fluid inlet of the first ejector; The gas outlet of the first flasher is connected to the gas channel inlet of the regenerator, and the gas channel outlet of the regenerator is connected to the air intake of the compressor.

2. The water source high temperature heat pump system according to claim 1, characterized in that: It also includes a first temperature detection member, a first pressure detection member and a first regulating valve, wherein the first temperature detection member and the first pressure detection member are arranged on a pipeline between the outlet of the evaporator and the ejected fluid inlet of the first ejector; The first regulating valve is disposed on a pipeline between a liquid outlet of the first flash evaporator and an inlet of the evaporator.

3. The water source high temperature heat pump system according to claim 2, characterized in that: It also includes a control module, wherein a first input end of the control module is electrically connected to the first temperature detection element, a second input end of the control module is electrically connected to the first pressure detection element, and a first output end of the control module is electrically connected to the first regulating valve; The control module is used to: obtain the actual fluid temperature detected by the first temperature detection component, obtain the actual fluid pressure detected by the first pressure detection component, determine the fluid saturation temperature based on the actual fluid pressure, and adjust the opening of the first regulating valve based on the actual fluid temperature and the fluid saturation temperature.

4. The water source high temperature heat pump system according to claim 3, characterized in that: It also includes an oil separator, a second ejector, a second flasher, and an oil cooler; The oil separator is connected between the compressor and the condenser, and the refrigerant inlet of the oil separator is connected to the exhaust port of the compressor, and the refrigerant outlet of the oil separator is connected to the inlet of the condenser; The oil outlet of the oil separator is connected to the oil channel inlet of the oil cooler, and the oil channel outlet of the oil cooler is connected to the oil return port of the compressor; The ejection fluid inlet of the second ejector is connected to the liquid channel outlet of the regenerator, the outlet of the second ejector is connected to the inlet of the second flasher, the liquid outlet of the second flasher is connected to the refrigerant channel inlet of the oil cooler, and the refrigerant channel outlet of the oil cooler is connected to the ejected fluid inlet of the second ejector; The gas outlet of the second flasher is connected to the gas supply port of the compressor.

5. The water source high temperature heat pump system according to claim 4, characterized in that: It also includes a second temperature detection member and a second regulating valve, wherein the second temperature detection member is arranged on a pipeline between the oil channel outlet of the oil cooler and the oil return port of the compressor; The second regulating valve is disposed on a pipeline between a liquid outlet of the second flasher and an inlet of a refrigerant passage of the oil cooler.

6. The water source high temperature heat pump system according to claim 5, characterized in that: The third input end of the control module is electrically connected to the second temperature detection element, and the second output end of the control module is electrically connected to the second regulating valve; The control module is specifically used to: obtain the measured oil supply temperature detected by the second temperature detection component, and adjust the opening of the second regulating valve based on the measured oil supply temperature and a preset oil supply temperature.

7. The water source high temperature heat pump system according to claim 6, characterized in that: The preset fuel supply temperature includes a preset maximum fuel supply temperature and a preset minimum fuel supply temperature. The control module is specifically used for: When the measured oil supply temperature is greater than or equal to the preset minimum oil supply temperature and less than or equal to the preset maximum oil supply temperature, the opening of the second regulating valve remains unchanged; When the measured oil supply temperature is greater than the preset maximum oil supply temperature, increasing the opening of the second regulating valve; When the measured oil supply temperature is lower than the preset minimum oil supply temperature, the opening of the second regulating valve is reduced.

8. The water source high temperature heat pump system according to any one of claims 4 to 7, characterized in that: It also includes a second pressure detection component and a third regulating valve, and the second pressure detection component and the third regulating valve are both arranged on the pipeline between the gas outlet of the second flasher and the gas supply port of the compressor.

9. The water source high temperature heat pump system according to claim 8, characterized in that: The fourth input end of the control module is electrically connected to the second pressure detection element, and the third output end of the control module is electrically connected to the third regulating valve; The control module is used to obtain the measured air supply pressure detected by the second pressure detection component, and adjust the opening of the third regulating valve based on the measured air supply pressure and the target air supply pressure.

10. The water source high temperature heat pump system according to claim 9, characterized in that: The control module is specifically used for: When the measured air supply pressure is greater than the target air supply pressure, reducing the opening of the third regulating valve; When the measured air supply pressure is less than the target air supply pressure, the opening of the third regulating valve is increased.

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