A water source high temperature heat pump system

Abstract

The utility model discloses a kind of water source high-temperature heat pump systems, the water source high-temperature heat pump system includes compressor, condenser, regenerator, first ejector, first flasher, evaporator;The exhaust port of compressor is connected with the inlet of condenser;The outlet of condenser is connected with the liquid channel inlet of regenerator, the liquid channel outlet of regenerator is connected with the injection fluid inlet of first ejector;The outlet of first ejector is connected with the inlet of first flasher, the liquid outlet of first flasher is connected with the inlet of evaporator, the outlet of evaporator is connected with the injected fluid inlet of first ejector;The gas outlet of first flasher is connected with the gas channel inlet of regenerator, the gas channel outlet of regenerator is connected with the suction port of compressor.By using the above scheme, the problem of large power consumption and poor system economy is solved.

Description

Technical Field

[0001] This utility model relates to the technical field of heat pumps, and in particular to a water source high-temperature heat pump system. Background Technology

[0002] Existing high-temperature heat pump systems mostly employ single-stage or quasi-two-stage compression cycles, including compressors, condensers, expansion valves, evaporators, economizers, etc.

[0003] However, existing high-temperature heat pump systems have a large high-low pressure ratio, high exhaust temperature, and high power consumption. In particular, when the boost temperature is high, the system's economy is relatively poor. Utility Model Content

[0004] This 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 flash evaporator, and an evaporator;

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

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

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

[0009] The gas outlet of the first flash evaporator is connected to the gas channel inlet of the regenerator, and the gas channel outlet of the regenerator is connected to the suction port of the compressor.

[0010] In an optional embodiment of this utility model, it further includes a first temperature detection element, a first pressure detection element, and a first regulating valve, wherein the first temperature detection element and the first pressure detection element are disposed on the pipeline between the outlet of the evaporator and the inlet of the ejected fluid of the first ejector.

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

[0012] In an optional embodiment of this utility model, a control module is further included. The first input terminal of the control module is electrically connected to the first temperature detection element, the second input terminal of the control module is electrically connected to the first pressure detection element, and the first output terminal of the control module is electrically connected to the first regulating valve.

[0013] In an optional embodiment of this utility model, it further includes an oil separator, a second ejector, a second flash evaporator, and an oil cooler;

[0014] 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, while the refrigerant outlet of the oil separator is connected to the inlet of the condenser.

[0015] The oil outlet of the oil separator is connected to the oil passage inlet of the oil cooler, and the oil passage outlet of the oil cooler is connected to the oil return port of the compressor.

[0016] The ejector 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 flash evaporator, the liquid outlet of the second flash evaporator 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.

[0017] The gas outlet of the second flash evaporator is connected to the gas supply port of the compressor.

[0018] In an optional embodiment of this utility model, a second temperature detection element and a second regulating valve are further included. The second temperature detection element is disposed on the pipeline between the oil passage outlet of the oil cooler and the oil return port of the compressor.

[0019] The second regulating valve is installed on the pipeline between the liquid outlet of the second flash evaporator and the refrigerant passage inlet of the oil cooler.

[0020] In an optional embodiment of this utility model, the third input terminal of the control module is electrically connected to the second temperature detection element, and the second output terminal of the control module is electrically connected to the second regulating valve; and / or, the second regulating valve includes an expansion valve.

[0021] In an optional embodiment of this utility model, a second pressure detection element and a third regulating valve are further included, wherein the second pressure detection element and the third regulating valve are both disposed on the pipeline between the gas outlet of the second flash generator and the gas supply port of the compressor.

[0022] In an optional embodiment of this utility model, the fourth input terminal of the control module is electrically connected to the second pressure detection element, and the third output terminal of the control module is electrically connected to the third regulating valve.

[0023] In an optional embodiment of this utility model, the first regulating valve includes an expansion valve.

[0024] In an optional embodiment of this utility model, the second regulating valve includes an expansion valve.

[0025] The technical solution of this utility model embodiment, by setting a first ejector, a first flash evaporator, an evaporator, and a regenerator, uses the condensed refrigerant as the ejector fluid. The refrigerant discharged from the outlet of the ejector evaporator is mixed with the first flash evaporator, where gaseous refrigerant and liquid refrigerant are separated. The gaseous refrigerant is superheated by the regenerator and then enters the suction port of the compressor, increasing the suction pressure of the compressor. Compared with related technologies, this reduces the high-low pressure ratio, thereby reducing the power consumption of the compressor, improving the coefficient of performance (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.

[0026] It should be understood that the description in this section is not intended to identify key or essential features of the embodiments of this utility model, nor is it intended to limit the scope of this utility model. Other features of this utility model will become readily apparent from the following description. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 This is a schematic diagram of a water source high-temperature heat pump system according to an embodiment of the present utility model;

[0029] Figure 2 This is a circuit block diagram of a water source high-temperature heat pump system provided according to an embodiment of the present utility model.

[0030] The components are as follows: 1. Compressor; 2. Oil separator; 3. Condenser; 4. Regenerator; 5. First ejector; 6. First flash evaporator; 7. First regulating valve; 8. Evaporator; 9. Second ejector; 10. Second flash evaporator; 11. Second regulating valve; 12. Oil cooler; 13. Third regulating valve; 14. First pressure sensor; 15. First temperature sensor; 16. Second temperature sensor; 17. Second pressure sensor; 18. Control module. Detailed Implementation

[0031] To enable those skilled in the art to better understand the present invention, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the protection scope of the present invention.

[0032] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this utility model are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of the utility model described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0033] Figure 1 This is a schematic diagram of a water source high-temperature heat pump system provided in an embodiment of the present invention. The water source high-temperature heat pump system is a heat pump system that uses water as a source for heating. The connections in this water source high-temperature heat pump system refer to connections via pipelines, 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 flash evaporator 6, and an evaporator 8.

[0034] The discharge port of compressor 1 is connected to the inlet of condenser 3; the outlet of condenser 3 is connected to the liquid passage inlet of regenerator 4. Compressor 1 consumes electrical energy to raise the temperature and pressure of the low-temperature, low-pressure refrigerant to a high-temperature, high-pressure state. The high-temperature, high-pressure refrigerant exchanges heat with cooling water in condenser 3, and the heat released by the refrigerant is absorbed by the water, causing the refrigerant to change from a gaseous state to a liquid state. The liquid refrigerant discharged from the outlet of condenser 3 enters the liquid passage inlet of regenerator 4.

[0035] The liquid outlet of the regenerator 4 is connected to the ejector fluid inlet of the first ejector 5. The outlet of the first ejector 5 is connected to the inlet of the first flash evaporator 6. The liquid outlet of the first flash evaporator 6 is connected to the inlet of the evaporator 8. The outlet of the evaporator 8 is connected to the ejected fluid inlet of the first ejector 5. The gas outlet of the first flash evaporator 6 is connected to the gas channel inlet of the regenerator 4. The gas channel outlet of the regenerator 4 is connected to the suction port of the compressor 1.

[0036] The first ejector 5 is a device that uses a high-speed, high-energy jet (liquid, gas, or other material flow) to eject another low-speed, low-energy jet. The jet enters the mixing chamber through a converging nozzle, surrounded by the entrained jet. Through the boundary mixing effect, the ejector transfers energy to the entrained jet. The main function of the first flash evaporator 6 is to use the heat released by a portion of the refrigerant condensing into liquid to vaporize another portion of the refrigerant into refrigerant vapor.

[0037] The refrigerant discharged from the liquid channel outlet of the regenerator 4 enters the ejector fluid inlet of the first ejector 5 as the ejector fluid, ejecting the refrigerant discharged from the outlet of the evaporator 8 to the ejected 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, separating 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 water and vaporize. The gaseous refrigerant discharged from the gas outlet of the first flash evaporator 6 enters through the gas channel inlet of the regenerator 4 and exchanges heat with the liquid refrigerant in the liquid channel of the regenerator 4. Then, it is discharged from the gas channel outlet of the regenerator 4 to the suction port of the compressor 1.

[0038] The above scheme, by setting up a first ejector 5, a first flash evaporator 6, an evaporator 8, and a regenerator 4, uses the condensed refrigerant as the ejector fluid to eject the refrigerant discharged from the outlet of the evaporator 8. After the mixed fluid passes through the first flash evaporator 6, gaseous refrigerant and liquid refrigerant are separated. The gaseous refrigerant is superheated by the regenerator 4 and then enters the suction port of the compressor 1. Therefore, the suction pressure of the compressor 1 is increased, and the high-low pressure ratio is reduced compared with related technologies, thereby reducing the power consumption of the compressor 1, improving the coefficient of performance (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.

[0039] In an optional embodiment of this utility model, such as Figure 1 As shown, the water source high-temperature heat pump system also includes a first temperature detection element 15, a first pressure detection element 14, and a first regulating valve 7. The first temperature detection element 15 and the first pressure detection element 14 are installed 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 installed on the pipeline between the liquid outlet of the first flash evaporator 6 and the inlet of the evaporator 8.

[0040] The first temperature detection element 15 refers to a component capable of detecting temperature. Preferably, the first temperature detection element 15 includes a temperature sensor, thereby enabling convenient temperature detection. By placing the first temperature detection element 15 in the pipeline between the outlet of the evaporator 8 and the inlet of the ejected fluid of the first ejector 5, the first temperature detection element 15 can detect the temperature of the fluid flowing through the pipeline between the outlet of the evaporator 8 and the inlet of the ejected fluid of the first ejector 5, i.e., the actual fluid temperature.

[0041] The first pressure detection element 14 refers to a component capable of detecting pressure. Preferably, the first pressure detection element 14 includes one of a pressure sensor and a pressure gauge, thereby enabling convenient pressure detection. By placing the first pressure detection element 14 in the pipeline between the outlet of the evaporator 8 and the inlet of the ejected fluid of the first ejector 5, the first pressure detection element 14 can detect the pressure of the fluid flowing through the pipeline between the outlet of the evaporator 8 and the inlet of the ejected fluid of the first ejector 5, i.e., the actual fluid pressure.

[0042] The first regulating valve 7 is a valve that controls the refrigerant flow rate in the pipeline between the liquid outlet of the first flash evaporator 6 and the inlet of the evaporator 8. When the first regulating valve 7 is open, the liquid refrigerant discharged from the liquid outlet of the first flash evaporator 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 flash evaporator 6 cannot enter the inlet of the evaporator 8. Furthermore, different opening degrees of the first regulating valve 7 will result in different refrigerant flow rates and pressures.

[0043] 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, thus achieving 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 flash evaporator 6 can be throttled before entering the inlet of the evaporator 8, so that the liquid refrigerant reaches the desired flow rate and pressure.

[0044] Based on the above embodiments, such as Figure 1 and Figure 2 As shown, the water source high-temperature heat pump system also includes a control module 18. The first input terminal of the control module 18 is electrically connected to the first temperature detection element 15, the second input terminal of the control module 18 is electrically connected to the first pressure detection element 14, and the first output terminal of the control module 18 is electrically connected to the first regulating valve 7.

[0045] In some embodiments, the control module 18 is configured to: acquire the actual fluid temperature detected by the first temperature sensor 15, acquire the actual fluid pressure detected by the first pressure sensor 14, determine the fluid saturation temperature based on the actual fluid pressure, and adjust the opening degree of the first regulating valve 7 based on the actual fluid temperature and the fluid saturation temperature.

[0046] The control module 18 refers to a functional module used for 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 one of a PLC and 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. This is not specifically limited here, but is only an example.

[0047] Fluid saturation temperature is the temperature at which the fluid reaches saturation. Saturation temperature refers to the temperature at which the number of vaporized molecules and the number of condensed molecules reach dynamic equilibrium during the evaporation process of a liquid. A certain saturation temperature of a substance necessarily corresponds to a certain saturation pressure. Therefore, by measuring the actual fluid pressure, the fluid saturation temperature can be obtained from the actual fluid pressure. In a heat pump system, when the fluid is a refrigerant, the actual fluid temperature is the actual refrigerant temperature, and the fluid saturation temperature is the refrigerant saturation temperature. The actual refrigerant temperature at the outlet of evaporator 8 needs to maintain a certain difference from the refrigerant saturation temperature. This ensures an appropriate refrigerant flow rate, allowing the refrigerant to effectively convert into vapor, thereby achieving a cooling effect. It is understood that in this embodiment, the actual fluid pressure refers to the pressure of the refrigerant flowing through the pipeline, which will not be elaborated further below.

[0048] When the opening degree of the first regulating valve 7 is different, the refrigerant flow rate 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 as currently measured, the refrigerant flow rate can be changed by adjusting the opening degree of the first regulating valve 7 based on the difference between the actual refrigerant temperature and the refrigerant saturation temperature, thereby improving the effectiveness of the evaporator 8 and achieving a more effective cooling effect.

[0049] For example, the control module 18 is specifically used to: increase the opening of the first regulating valve 7 when the difference between the actual refrigerant temperature and the refrigerant saturation temperature is greater than the target maximum value; decrease 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 target minimum value; and keep the opening of the first regulating valve 7 unchanged when the difference between the actual refrigerant temperature and the refrigerant saturation temperature is greater than or equal to the target minimum value and less than or equal to the target maximum value.

[0050] When the difference between the actual refrigerant temperature and the refrigerant saturation temperature is greater than the maximum target value, it indicates that the refrigerant flow rate entering the evaporator 8 is too low. Therefore, the opening of the first regulating valve 7 is increased to improve the actual refrigerant flow rate, thereby ensuring that the evaporator 8 is in a phase change heat transfer state, allowing the refrigerant in the evaporator 8 to be converted into steam more effectively, thus achieving the cooling effect.

[0051] When the difference between the actual refrigerant temperature and the refrigerant saturation temperature is less than the minimum target value, it indicates that the refrigerant flow rate entering the evaporator 8 is too high. Therefore, the opening of the first regulating valve 7 is reduced to decrease the actual refrigerant flow rate, so that the area of ​​the evaporator 8 is fully utilized, allowing the refrigerant in the evaporator 8 to be converted into vapor more effectively, thereby achieving the cooling effect.

[0052] In an optional embodiment of this utility model, such as Figure 1 As shown, the water source high-temperature heat pump system also includes an oil separator 2, a second ejector 9, a second flash evaporator 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 passage inlet of the oil cooler 12, and the oil passage outlet of the oil cooler 12 is connected to the oil return port of the compressor 1.

[0053] In this process, compressor 1 consumes electrical energy to raise the low-temperature, low-pressure refrigerant to a high-temperature, high-pressure state. The high-temperature, high-pressure refrigerant then passes through oil separator 2, where it separates the lubricating oil from the high-pressure refrigerant discharged from compressor 1. The refrigerant is then discharged to condenser 3, where it exchanges heat with cooling water. The heat released by the refrigerant is absorbed by the water, causing it to change from a gaseous state to a liquid state. The liquid refrigerant discharged from condenser 3 enters the liquid channel inlet of regenerator 4. The lubricating oil discharged from oil separator 2 enters the oil channel inlet of oil cooler 12 and then exits from the oil channel outlet of oil cooler 12 back to the oil return port of compressor 1.

[0054] The ejector 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 flash evaporator 10, the liquid outlet of the second flash evaporator 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, and the gas outlet of the second flash evaporator 10 is connected to the gas supply port of the compressor 1.

[0055] The refrigerant discharged from the liquid channel outlet of the regenerator 4 enters the ejector fluid inlet of the second ejector 9 as the ejector fluid, ejecting the refrigerant discharged from the refrigerant channel outlet of the oil cooler 12 to the ejected 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 and separates into gaseous refrigerant and 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 gas injection port of the compressor 1.

[0056] The above scheme cools the lubricating oil entering the oil cooler 12 by the refrigerant entering the oil cooler 12, which can ensure that the oil supply temperature of the compressor 1 is within the limit range. At the same time, the gaseous refrigerant discharged from the gas outlet of the second flash evaporator 10 is discharged to the gas supply port of the compressor 1, and the compressor 1 is used to supply gas, which further reduces the discharge temperature of the compressor 1.

[0057] In an optional embodiment of this utility model, the water source high-temperature heat pump system further includes a second temperature detection element 16 and a second regulating valve 11. The second temperature detection element 16 is disposed 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 disposed on the pipeline between the liquid outlet of the second evaporator 10 and the refrigerant channel inlet of the oil cooler 12.

[0058] The second temperature detection element 16 refers to a component capable of detecting temperature. Preferably, the second temperature detection element 16 includes a temperature sensor, thereby enabling convenient temperature detection. By placing the second temperature detection element 16 on the pipeline between the oil passage outlet of the oil cooler 12 and the oil return port of the compressor 1, the second temperature detection element 16 can detect the temperature of the lubricating oil discharged from the oil passage outlet of the oil cooler 12 to the compressor 1, that is, it can measure the oil supply temperature, and the measured oil supply temperature is the actual oil supply temperature.

[0059] The second regulating valve 11 is a valve that controls the refrigerant flow between the liquid outlet of the second flash evaporator 10 and the refrigerant channel inlet of the oil cooler 12. In some embodiments, the second regulating valve 11 is an expansion valve. The expansion valve mainly controls the flow rate and pressure of the fluid by reducing the flow area, thereby achieving 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. When the second regulating valve 11 is open, the refrigerant discharged from the liquid outlet of the second flash evaporator 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 flash evaporator 10 cannot enter the refrigerant channel inlet of the oil cooler 12. Furthermore, different opening degrees of the second regulating valve 11 result in different flow rates of refrigerant entering the oil cooler 12, which in turn affects the heat exchange effect on the lubricating oil in the oil cooler 12, meaning that the temperature of the lubricating oil after passing through the oil cooler 12 will vary.

[0060] Based on the above embodiments, such as Figure 1 and Figure 2 As shown, the third input terminal of the control module 18 is electrically connected to the second temperature sensor 16, and the second output terminal of the control module 18 is electrically connected to the second regulating valve 11.

[0061] For example, the control module 18 is specifically used to: acquire the measured oil supply temperature detected by the second temperature sensor 16, and adjust the opening of the second regulating valve 11 based on the measured oil supply temperature and the preset oil supply temperature.

[0062] The preset oil supply temperature refers to the oil supply temperature at which the lubricating oil has a suitable viscosity, enabling better lubrication of mechanical parts, reducing wear, and extending the service life of compressor 1. The preset oil supply temperature may vary depending on the type of compressor 1 and the lubricating oil used; therefore, no specific value for the preset oil supply temperature is specified here.

[0063] The measured oil supply temperature is the actual oil supply temperature of the current lubricating oil, while the preset oil supply temperature is the ideal oil supply temperature. When the opening degree of the second regulating valve 11 is different, the cooling effect on the lubricating oil of the oil cooler 12 is different, resulting in different oil supply temperatures. Therefore, adjusting the opening degree 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 a suitable range, which helps to maintain the stable operation of the compressor 1, reduce performance changes and failures caused by excessively high or low oil temperatures, and improve the stability of the entire system.

[0064] For example, the preset oil supply temperature includes a maximum preset oil supply temperature and a minimum preset oil supply temperature. The control module 18 is specifically used to: keep the opening of the second regulating valve 11 unchanged when the measured oil supply temperature is greater than or equal to the minimum preset oil supply temperature and less than or equal to the maximum preset oil supply temperature; increase the opening of the second regulating valve 11 when the measured oil supply temperature is greater than the maximum preset oil supply temperature; and decrease the opening of the second regulating valve 11 when the measured oil supply temperature is less than the minimum preset oil supply temperature.

[0065] The preset maximum 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. The preset minimum 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 oil supply temperature, it indicates 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 improving the cooling effect on the lubricating oil. The temperature of the lubricating oil discharged from the oil cooler 12 to the compressor 1 decreases, that is, the actual oil supply temperature decreases. Thus, the measured oil supply temperature can get closer to the preset maximum 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.

[0066] When the measured oil supply temperature is less than the preset minimum oil supply temperature, it indicates that the oil supply temperature is too low. At this time, reducing the opening of the second regulating valve 11 will reduce the amount of refrigerant entering the oil cooler 12, thereby increasing the temperature of the lubricating oil discharged from the oil cooler 12 to the compressor 1, i.e., increasing the actual oil supply temperature. As a result, the measured oil supply temperature can get 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.

[0067] The above scheme can effectively control the temperature of the lubricating oil entering the compressor 1, so that the actual 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. This ensures that the actual oil supply temperature is within a suitable range, which helps to maintain the stable operation of the compressor 1, reduce performance changes and malfunctions caused by excessively high or low oil temperatures, and improve the stability of the entire system.

[0068] In optional embodiments of this utility model, such as Figure 1 and Figure 2 As shown, the water source high-temperature heat pump system also includes a second pressure detection element 17 and a third regulating valve 13. The second pressure detection element 17 and the third regulating valve 13 are both installed on the pipeline between the gas outlet of the second evaporator 10 and the gas supply port of the compressor 1.

[0069] The second pressure detection element 17 refers to a component capable of detecting pressure. Preferably, the second pressure detection element 17 includes one of a pressure sensor and a pressure gauge, thereby enabling convenient pressure detection. By placing the second pressure detection element 17 in the pipeline between the gas outlet of the second flash evaporator 10 and the gas supply port of the compressor 1, the second pressure detection element 17 can detect the pressure of the gaseous refrigerant flowing through the pipeline between the gas outlet of the second flash evaporator 10 and the gas supply port of the compressor 1, that is, it can actually measure the pressure at which gas is supplied to the compressor 1, and the obtained pressure value is the measured gas supply pressure.

[0070] The third regulating valve 13 refers to a valve that can control the pipeline resistance between the gas outlet of the second flash generator 10 and the gas supply port of the compressor 1. In this embodiment, the third regulating valve 13 is a valve that can control the flow rate and pressure of the fluid.

[0071] When the third regulating valve 13 is open, the gaseous refrigerant discharged from the gas outlet of the second flash evaporator 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 flash evaporator 10 cannot enter the gas supply port of the compressor 1, that is, it cannot supply gas to the compressor 1. In addition, the pressure of the gaseous refrigerant entering the compressor 1 is different depending on the opening degree of the third regulating valve 13, that is, the gas supply pressure for supplying gas to the compressor 1 is different.

[0072] Based on the above embodiments, such as Figure 1 and Figure 2 As shown, the fourth input terminal of the control module 18 is electrically connected to the second pressure detection element 17, and the third output terminal of the control module 18 is electrically connected to the third regulating valve 13; the control module 18 is used to: acquire the measured replenishment pressure detected by the second pressure detection element 17, and adjust the opening of the third regulating valve 13 based on the measured replenishment pressure and the target replenishment pressure.

[0073] The target injection pressure refers to the pressure that the gaseous refrigerant entering the injection port of compressor 1 should reach. The measured injection pressure is the actual pressure of the gaseous refrigerant entering the injection port of compressor 1. By adjusting the opening of the third regulating valve 13 based on the measured and target injection pressures, the injection pressure of compressor 1 can be controlled. By controlling the injection pressure, the operating state of compressor 1 can be optimized, the undercompression process can be reduced, and the increase in the volumetric power of compressor 1 can be decreased, thereby improving the efficiency and stability of the system. Simultaneously, during the undercompression process, injection pressure control can reduce the power consumption of compressor 1, thereby reducing the overall energy consumption of the system. In a water source high-temperature heat pump system, injection pressure control can optimize the system's thermodynamic performance, improve the heating efficiency ratio, and meet industrial heating needs. Finally, injection pressure control enables the system to better adapt to different workloads and changes in water source temperature, maintaining the normal operation of the system.

[0074] For example, the control module 18 is specifically used to: decrease the opening of the third regulating valve 13 when the measured replenishment pressure is greater than the target replenishment pressure; and increase the opening of the third regulating valve 13 when the measured replenishment pressure is less than the target replenishment pressure. Furthermore, when the measured replenishment pressure is equal to the target replenishment pressure, the opening of the third regulating valve 13 remains unchanged.

[0075] Specifically, if the measured replenishment pressure is greater than the target replenishment pressure, it indicates that the actual replenishment pressure is too high. In this case, reducing the opening of the third regulating valve 13 will decrease the replenishment pressure. Conversely, if the measured replenishment pressure is less than the target replenishment pressure, it indicates that the actual replenishment pressure is too low. In this case, increasing the opening of the third regulating valve 13 will increase the replenishment pressure. Therefore, by controlling the opening of the third regulating valve 13, the replenishment pressure can be adjusted so that the measured replenishment pressure equals the target replenishment pressure, effectively improving the system performance.

[0076] It should be understood that the various forms of the process shown above can be used, with steps reordered, added, or deleted. For example, the steps described in this utility model can be executed in parallel, sequentially, or in different orders, as long as the desired result of the technical solution of this utility model can be achieved, and this is not limited herein.

[0077] The specific embodiments described above do not constitute a limitation on the scope of protection of this utility model. Those skilled in the art should understand that various modifications, combinations, sub-combinations, and substitutions can be made according to design requirements and other factors. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the scope of protection of this utility model.

Claims

1. A water source high-temperature heat pump system, characterized in that, Includes a compressor, condenser, regenerator, first ejector, first flash evaporator, and evaporator; The compressor's exhaust port is connected to the condenser's inlet; The outlet of the condenser is connected to the liquid channel inlet of the regenerator, and the liquid channel outlet of the regenerator is connected to the ejector fluid inlet of the first ejector. The outlet of the first ejector is connected to the inlet of the first flash evaporator, the liquid outlet of the first flash evaporator is connected to the inlet of the evaporator, and the outlet of the evaporator is connected to the inlet of the ejected fluid of the first ejector. The gas outlet of the first flash evaporator is connected to the gas channel inlet of the regenerator, and the gas channel outlet of the regenerator is connected to the suction port 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 sensor, a first pressure sensor, and a first regulating valve, wherein the first temperature sensor and the first pressure sensor are disposed on the pipeline between the outlet of the evaporator and the inlet of the ejected fluid of the first ejector; The first regulating valve is installed on the pipeline between the liquid outlet of the first flash evaporator and the 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, the first input terminal of which is electrically connected to the first temperature detection element, the second input terminal of which is electrically connected to the first pressure detection element, and the first output terminal of which is electrically connected to the first regulating valve.

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 flash evaporator, 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, while 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 passage inlet of the oil cooler, and the oil passage outlet of the oil cooler is connected to the oil return port of the compressor. The ejector 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 flash evaporator, the liquid outlet of the second flash evaporator 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 flash evaporator 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 element and a second regulating valve, wherein the second temperature detection element is disposed on the pipeline between the oil passage outlet of the oil cooler and the oil return port of the compressor; The second regulating valve is installed on the pipeline between the liquid outlet of the second flash evaporator and the refrigerant passage inlet of the oil cooler.

6. The water source high-temperature heat pump system according to claim 5, characterized in that, The third input terminal of the control module is electrically connected to the second temperature detection element, and the second output terminal of the control module is electrically connected to the second regulating valve.

7. The water source high-temperature heat pump system according to any one of claims 4 to 6, characterized in that, It also includes a second pressure detection element and a third regulating valve, both of which are installed on the pipeline between the gas outlet of the second flash evaporator and the gas supply port of the compressor.

8. The water source high-temperature heat pump system according to claim 7, characterized in that, The fourth input terminal of the control module is electrically connected to the second pressure detection element, and the third output terminal of the control module is electrically connected to the third regulating valve.

9. The water source high-temperature heat pump system according to any one of claims 2 to 6, characterized in that, The first regulating valve includes an expansion valve.

10. The water source high-temperature heat pump system according to claim 5 or 6, characterized in that, The second regulating valve includes an expansion valve.

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