Steam generating equipment

Abstract

The utility model provides steam generation equipment which comprises a heat pump system, a heat pump system and a heat pump system, the heat pump system comprises a compressor, a steam generator, a throttling element and an evaporator, the compressor, the steam generator, the throttling element and the evaporator are sequentially connected to form a refrigerant circulation loop for circulating flowing of refrigerants, the steam generator heats water into steam through the refrigerants, and the steam generator is provided with a water supplementing opening; the water replenishing system comprises a water tank, a water replenishing pump and a water replenishing pipeline, the water replenishing pipeline is connected with the water tank and the water replenishing port and is thermally coupled with at least one to-be-cooled object of the heat pump system, and the water replenishing pump is arranged on the water replenishing pipeline to drive water in the water tank to directly or indirectly cool the at least one to-be-cooled object; and the water cooling the at least one to-be-cooled object is driven to flow to the water replenishing port to replenish water to the steam generator. Therefore, the energy efficiency can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of steam preparation, and in particular to a steam generating device. Background Art

[0002] With the rapid development of industrial technology, the demand for steam is increasing. Steam generating equipment is a device that generates steam to meet the demand.

[0003] However, the energy efficiency of steam generation equipment needs to be improved. Utility Model Content

[0004] A technical problem to be solved by this application is to improve the energy efficiency of steam generating equipment.

[0005] In order to solve the above technical problems, the present application provides a steam generating device, which includes:

[0006] A heat pump system comprising a compressor, a steam generator, a throttling device and an evaporator, wherein the compressor, the steam generator, the throttling device and the evaporator are sequentially connected to form a refrigerant circulation loop for circulating refrigerant, the steam generator utilizes the refrigerant to heat water into steam, and the steam generator has a water supply port; and

[0007] The water supply system includes a water tank, a water supply pump and a water supply pipeline. The water supply pipeline connects the water tank and the water supply port and is thermally coupled to at least one object to be cooled in the heat pump system. The water supply pump is arranged on the water supply pipeline to drive the water in the water tank to directly or indirectly cool the at least one object to be cooled, and drives the water after cooling the at least one object to be cooled to flow to the water supply port to supply water to the steam generator.

[0008] In some embodiments, at least one object to be cooled includes a motor of a compressor, and the refrigerant outlet of the steam generator is thermally coupled to the motor through a cooling pipeline so as to utilize the refrigerant flowing out of the steam generator to cool the motor. The water supply pipeline includes a first water supply pipeline, which connects the water tank and the water supply port. A first heat exchanger is provided on the first water supply pipeline, and the first heat exchanger is connected to the cooling pipeline so that the water in the water tank flows through the first heat exchanger in the process of flowing to the water supply port, and cools the refrigerant flowing from the refrigerant outlet to the motor at the first heat exchanger.

[0009] In some embodiments, the water replenishment pipeline further includes a first water return pipeline, which is connected to the water tank and to the portion of the first water supply pipeline located between the first heat exchanger and the water replenishment port to guide the water flowing out of the first heat exchanger back to the water tank.

[0010] In some embodiments, the water replenishment system further includes a first valve, which is disposed at the connection between the first return water pipeline and the first water supply pipeline to control the flow from the first heat exchanger to the water replenishment port and the first return water pipeline.

[0011] In some embodiments, the heat pump system includes an oil tank, which is connected to the compressor through a lubrication pipeline to supply lubricating oil to the compressor to lubricate the compressor. At least one object to be cooled includes lubricating oil. The water supply pipeline includes a second water supply pipeline, which is connected to the water tank. A second heat exchanger is provided on the second water supply pipeline, and the second heat exchanger is connected to the lubrication pipeline so that the lubricating oil flowing to the compressor is cooled by water in the second water supply pipeline flowing from the water tank.

[0012] In some embodiments, the second water supply line is connected to a portion of the first water supply line of the water supply line located between the first heat exchanger and the water tank.

[0013] In some embodiments, the water replenishment system further includes a second valve, which is disposed at the connection between the first water supply pipeline and the second water supply pipeline and controls the flow from the water tank to the first heat exchanger and the second heat exchanger.

[0014] In some embodiments, the water supply pipeline further includes a second water return pipeline, which connects the second heat exchanger and the water tank to guide the water after cooling the lubricating oil back to the water tank.

[0015] In some embodiments, the steam generator includes a shell and a heat exchange tube. The shell is used to hold water. The water supply port is set on the shell. The heat exchange tube is connected to the shell and to the outlet and throttling device of the compressor so that the high-temperature gaseous refrigerant discharged by the compressor flows into the heat exchange tube and heats the water in the shell into steam.

[0016] In some embodiments, the water makeup pump is a fixed frequency pump.

[0017] By setting up a heat pump system in the steam generating equipment to prepare steam, and constructing the water supply system of the steam generating equipment so that the supply water cools the object to be cooled by the heat pump system before flowing into the water supply port, the supply water temperature can be effectively increased, thereby effectively improving the energy efficiency of the steam generating equipment.

[0018] Other features and advantages of the present application will become apparent from the following detailed description of exemplary embodiments of the present application with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0020] Figure 1 This is a diagram showing the working principle of the steam generating equipment in an embodiment of the present application.

[0021] Description of reference numerals:

[0022] 10. Steam generating equipment;

[0023] 1. Heat pump system; 11. Compressor; 111. Outlet; 112. Inlet; 12. Steam generator; 121. Housing; 122. Refrigerant inlet; 123. Refrigerant outlet; 124. Water supply port; 125. Exhaust port; 126. Liquid level gauge; 127. Pressure regulating valve; 13. Throttle element; 14. Evaporator; 15. Refrigerant circulation loop; 16. Oil tank; 17. Oil pump; 18. Cooling line; 19. Lubrication line

[0024] 2. Water supply system; 20. Check valve; 21. Water treatment device; 22. Water tank; 23. Water supply pump; 24. Water supply pipeline; 241. First water supply pipeline; 242. Second water supply pipeline; 243. First return pipeline; 244. Second return pipeline; 25. First heat exchanger; 26. Second heat exchanger; 27. First valve; 28. Second valve; 29. ​​Drain valve;

[0025] 3. The first temperature measuring component;

[0026] 4. Second temperature measuring component;

[0027] 5. The third temperature measuring component. DETAILED DESCRIPTION

[0028] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without carrying out creative work are within the scope of protection of this application.

[0029] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered part of the specification.

[0030] In the description of this application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of this application; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0031] In the description of this application, it should be understood that the use of words such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above words have no special meaning and therefore cannot be understood as limiting the scope of protection of this application.

[0032] In addition, the technical features involved in the different embodiments of the present application described below can be combined with each other as long as they do not conflict with each other.

[0033] In the industrial field, steam is needed in processes such as wine distillation, Chinese medicine extraction, printing and dyeing bleaching, and steam sterilization. Moreover, with the development of industrial technology, the demand for high-temperature steam is increasing.

[0034] Steam generating equipment is a device used to generate steam. The steam it generates is supplied to steam consuming equipment (such as wine distillation equipment, Chinese medicine extraction equipment, printing and dyeing bleaching equipment or steam sterilization equipment) to meet the working needs of the corresponding steam consuming equipment.

[0035] Currently common steam generating equipment usually includes boilers or heat pumps.

[0036] Among them, although boilers can generate steam at relatively high temperatures, they usually use fossil fuels such as coal, so there are problems of serious pollution and low energy efficiency.

[0037] As a renewable energy utilization device, heat pumps can upgrade low-grade waste heat energy in various industrial production processes into high-grade heat energy through a small amount of electricity consumption, thereby doubling the heat and improving the quality. Under the same heating conditions, heat pump heat production can reduce electricity consumption by 30% to 85% compared with "direct electric heating", making it the most efficient way to supply heat. Therefore, heat pumps have shown great potential to replace boilers and prepare steam.

[0038] However, heat pumps themselves typically don't have steam generation capabilities. To achieve this, they typically require a flash tank and a circulating water pump. The flash tank and the heat pump's condenser are connected via piping to form a circulating water circuit. Hot water from the condenser flows through the circulating water circuit into the flash tank, where it flashes to generate steam. The steam is then discharged, while the remaining water settles at the bottom of the flash tank. Driven by the circulating water pump, it flows back to the condenser. The consumed steam is then replenished by the water supply system.

[0039] For example, for the demand for high-temperature steam of more than 2T / h at 115℃~145℃ in processes such as wine distillation, Chinese medicine extraction, printing and dyeing bleaching, and steam sterilization, the heat pump unit commonly uses the following steam production method: recover industrial waste heat of about 65℃, and use the heat pump unit to first generate 150℃ high-temperature hot water in the condenser on the refrigerant circulation loop. The 150℃ high-temperature hot water then enters the flash tank to flash out 145℃ saturated steam. After the hot water flashes the steam, its own water temperature also drops to 145℃ and remains at the bottom of the flash tank. The hot water at the bottom is then returned to the condenser of the heat pump unit through a circulation pump for heating, and the consumed steam is replenished into the flash tank by the water supply system.

[0040] The above heat pump steam generation method has the following problems:

[0041] (1) The feed water temperature used to compensate for the consumed steam is relatively low. The time required to generate high-temperature steam from the corresponding feed water is long, and the heat consumed is relatively high. For example, the general feed water temperature is usually around 20°C. The time and heat required to directly convert the feed water at around 20°C into high-temperature steam at 145°C are relatively long. Therefore, the efficiency and energy efficiency are both low.

[0042] (2) The heat pump itself only produces hot water, not steam, and needs to be equipped with a flash tank and a circulation pump, and needs to be equipped with more engineering pipelines, resulting in a complex structure and high cost;

[0043] (3) Since the heat pump unit does not generate steam, the heat pump unit does not need to replenish water. In this case, the heat pump unit does not have a cold source for replenishing water. The object to be cooled (including but not limited to the motor and lubricating oil) can only be cooled by conventional refrigerant. That is, the refrigerant can usually only be taken from the condenser. After the corresponding refrigerant is throttled and cooled, it is used to cool the object to be cooled. However, since the refrigerant taken out from the condenser is a high-temperature and high-pressure refrigerant, even after throttling, it can only be reduced to the evaporation temperature of the evaporator at the lowest. The evaporation temperature of the evaporator is close to the temperature of the heat source on the evaporator side. Therefore, the cooling effect of this method of taking refrigerant from the condenser to cool the object to be cooled is affected by the temperature of the heat source on the evaporator side. When the temperature of the heat source on the evaporator side is high, the cooling effect is poor and it is difficult to meet the cooling needs of the object to be cooled.

[0044] It can be seen that the use of a heat pump in combination with a flash tank to prepare steam has problems such as low energy efficiency, complex structure, high cost, a single cooling method for the object to be cooled, and poor cooling effect.

[0045] In response to the above situation, the present application provides a steam generating device and a control method thereof, a controller, a steam generating system and a storage medium.

[0046] Figure 1 The structure and working principle of the steam generating equipment in this application are exemplarily shown.

[0047] See also Figure 1 The steam generating device 10 includes a heat pump system 1 and a water supply system 2. The heat pump system 1 includes a compressor 11, a steam generator 12, a throttling device 13, and an evaporator 14. The compressor 11, steam generator 12, throttling device 13, and evaporator 14 are sequentially connected to form a refrigerant circulation loop 15 for circulating refrigerant. The steam generator 12 uses the refrigerant to heat water into steam. The steam generator 12 has a water supply port 124. The water supply system 2 includes a water tank 22, a water supply pump 23, and a water supply pipeline 24. The water supply pipeline 24 connects the water tank 22 and the water supply port 124 and is thermally coupled to at least one object to be cooled in the heat pump system 1. The water supply pump 23 is arranged on the water supply pipeline 24 to drive the water in the water tank 22 to directly or indirectly cool the at least one object to be cooled, and drives the water after cooling the at least one object to be cooled to flow to the water supply port 124 to supply water to the steam generator 12.

[0048] In the above solution, the steam generating device 10 uses the heat pump system 1 to prepare steam. This can effectively reduce pollution and improve energy efficiency compared to the method of preparing steam with a boiler.

[0049] Furthermore, since the make-up water used to compensate for the consumed steam does not flow directly to the make-up water port 124 of the heat pump system 1, but first cools the object to be cooled of the heat pump system 1 before flowing to the make-up water port 124 of the heat pump system 1, in the corresponding process, the make-up water can absorb the heat of the object to be cooled. Therefore, the make-up water can be preheated, and the temperature of the make-up water can be effectively increased, so that the temperature of the make-up water flowing into the make-up water port 124 is higher. In this way, the thermal energy quality of the make-up water is effectively improved, and it can better exchange heat with the refrigerant. It can evaporate to generate steam of the required temperature in a shorter time and with less heat consumption, so that energy efficiency can be further improved.

[0050] It can be seen that by setting up a heat pump system 1 in the steam generating device 10 to prepare steam, and constructing the water supply system 2 of the steam generating device 10 so that the supply water first cools the object to be cooled in the heat pump system 1 before flowing into the water supply port 124, the energy efficiency of the steam generating device 10 can be effectively improved.

[0051] In addition, the water supplied to the steam generator 12 is preheated in advance and the temperature is increased. From another perspective, when the same amount of heat is consumed, it is conducive to preparing steam with a higher temperature, which can better meet the demand of steam-consuming equipment for using higher temperature steam.

[0052] Moreover, the make-up water system 2 is used to cool the object to be cooled of the heat pump system 1 to achieve preheating of the make-up water. The object to be cooled of the heat pump system 1 is no longer limited to the refrigerant cooling method, which effectively increases the diversity of cooling methods. When the heat source temperature on the evaporator side is high and the evaporation temperature is high and cannot meet the cooling needs of the object to be cooled, make-up water cooling can be used to effectively improve the cooling effect of the object to be cooled.

[0053] In addition, in the above scheme, since the heat pump system 1 no longer relies on a flash tank to prepare steam, but instead replaces the original condenser of the heat pump unit located in the refrigerant circulation loop 15 with a steam generator 12 that can generate steam, the steam is prepared by the steam generator 12. Therefore, the heat pump system 1 has its own steam generation function and does not need to be equipped with a flash tank and a circulating water supply pump to generate steam. Therefore, it can effectively simplify the structure and reduce costs.

[0054] It can be seen that the above scheme replaces the original condenser in the heat pump system 1 with the steam generator 12, and constructs the make-up water system 2 so that the make-up water first cools the object to be cooled in the heat pump system 1 before flowing into the make-up water inlet 124. The heat pump system 1 itself can have an integrated steam generation function, and the object to be cooled in the heat pump system 1 can be cooled by the make-up water, and the make-up water can be preheated. In this way, the structure of the steam generating device 10 can be effectively simplified, the cost of the steam generating device 10 can be reduced, the cooling effect of the object to be cooled can be improved, the steam generation time can be shortened, the heat consumed in steam generation can be reduced, and the steam temperature can be increased. Therefore, the steam generating device 10 can achieve a more energy-efficient and efficient steam preparation and cooling process of the object to be cooled based on a simpler structure and lower cost.

[0055] It is understood that the objects to be cooled in the heat pump system 1 generally include, but are not limited to, the motor of the compressor 11 and the lubricating oil used to lubricate the compressor 11. Water supplementation can be used to cool different objects to be cooled, and the same or different methods can be used to cool each object to be cooled. For example, water supplementation can be used to cool all objects to be cooled directly or indirectly, or water supplementation can be used to cool some objects to be cooled indirectly and to cool other objects to be cooled directly.

[0056] Specifically, see, for example, Figure 1In some embodiments, the at least one object to be cooled includes a motor of the compressor 11 (not shown), and the refrigerant outlet 123 of the steam generator 12 is thermally coupled to the motor through the cooling pipe 18 to utilize the refrigerant flowing out of the steam generator 12 to cool the motor, and the water supply pipe 24 includes a first water supply pipe 241, which connects the water tank 22 and the water supply port 124. A first heat exchanger 25 is provided on the first water supply pipe 241, and the first heat exchanger 25 is connected to the cooling pipe 18, so that the water in the water tank 22 flows through the first heat exchanger 25 in the process of flowing to the water supply port 124, and cools the refrigerant flowing from the refrigerant outlet 123 to the motor at the first heat exchanger 25.

[0057] Based on the above arrangement, the water supply line 24 is thermally coupled to the motor of the compressor 11 through the first heat exchanger 25 and the cooling line 18 located on the first water supply line 241, so that the water flowing to the water supply port 124 can be cooled by exchanging heat with the refrigerant flowing out of the steam generator 12 at the first heat exchanger 25 for cooling the motor of the compressor 11. In the corresponding process, since the water supply can absorb the heat of the refrigerant at the first heat exchanger 25 and reduce the temperature of the refrigerant, the temperature of the refrigerant flowing to the motor of the compressor 11 can be lowered, thereby effectively improving the cooling of the compressor. The cooling effect of the motor of compressor 11 is such that even if the evaporation temperature is too high to meet the cooling demand of the motor of compressor 11, the refrigerant used to cool the motor of compressor 11 can be cooled by the make-up water, so as to effectively meet the cooling demand of the motor of compressor 11, prevent the motor from malfunctioning due to overheating, improve the reliability of compressor 11, and extend the life of compressor 11; and, the make-up water after cooling the motor of compressor 11 is preheated, the temperature is increased, and then flows into the steam generator 12, the time for heat to be converted into steam can be shortened, and the heat consumption can be reduced, thereby effectively improving the efficiency and energy efficiency of steam preparation.

[0058] At the same time, the above scheme realizes cooling of the compressor motor by exchanging heat between the make-up water and the refrigerant used to cool the compressor motor at the first heat exchanger 25. Since the make-up water does not need to directly cool the motor of the compressor 11, but indirectly cools the motor of the compressor 11 through the refrigerant, it can also prevent safety accidents caused by the make-up water entering the motor. Moreover, in this case, the flow path originally used to realize the refrigerant cooling of the compressor motor does not need to be changed. Therefore, the structural changes are relatively small, which can reduce the improvement cost.

[0059] It can be seen that by arranging a first heat exchanger 25 on the first water supply pipe 241 connecting the water tank 22 and the water supply port 124, and connecting the first heat exchanger 25 to the cooling pipe 18 for transporting the refrigerant to the motor of the compressor 11 to cool the motor, a safer and more efficient motor cooling and water supply preheating process can be achieved based on fewer structural changes, effectively improving the cooling effect of the motor of the compressor 11, and improving the efficiency and energy efficiency of steam preparation.

[0060] Further, see Figure 1 In some embodiments, the water replenishment pipeline 24 includes not only a first water supply pipeline 241, but also a first water return pipeline 243. The first water return pipeline 243 is connected to the water tank 22 and is connected to the portion of the first water supply pipeline 241 located between the first heat exchanger 25 and the water replenishment port 124 to guide the water flowing out of the first heat exchanger 25 back to the water tank 22.

[0061] Based on the above arrangement, the water preheated by the motor and flowing out of the first heat exchanger 25 can be diverted according to actual needs, so that when the steam generator 12 does not need to be replenished with water or the required amount of replenished water is small, the water flowing out of the first heat exchanger 25 can at least partially flow back to the water tank 22 via the first return water pipe 243. In this way, the water replenishment demand of the steam generator 12 can be met conveniently and flexibly, and energy waste can be reduced.

[0062] It is understood that whether the steam generator 12 requires water replenishment and the amount of water replenishment vary depending on the steam consumption of the steam-consuming equipment. The more steam a steam-consuming equipment consumes, the more water replenishment is required. If no steam is consumed, no water replenishment is required. Therefore, in addition to the first water supply pipeline 241, a first water return pipeline 243 is further provided to effectively meet the needs of situations where the amount of water flowing out of the first heat exchanger 25 exceeds the required water replenishment amount.

[0063] Further, see Figure 1 In some embodiments, the water replenishment system 2 not only includes a first water supply pipeline 241 and a first return water pipeline 243, but also includes a first valve 27. The first valve 27 is arranged at the connection between the first return water pipeline 243 and the first water supply pipeline 241 to control the flow from the first heat exchanger 25 to the water replenishment port 124 and the first return water pipeline 243.

[0064] The first valve 27 is provided to automatically adjust the distribution of water flowing out of the first heat exchanger 25 between the two paths flowing to the water replenishment port 124 and flowing back to the water tank 22. Therefore, it is more convenient to achieve a timely and accurate flow distribution process and better meet different water replenishment needs.

[0065] In addition, as previously mentioned, the object to be cooled by the heat pump system 1 may not only be the motor of the compressor 11 but also the lubricating oil used to lubricate the compressor 11. The corresponding lubricating oil is generally stored in an oil tank 16, which is connected to the compressor 11 via a lubrication line 19 to supply the lubricating oil to the compressor 11 for lubrication.

[0066] In order to realize the water supply cooling method for lubricating oil, see Figure 1 In some embodiments, the water supply line 24 includes a second water supply line 242, which is connected to the water tank 22. A second heat exchanger 26 is provided on the second water supply line 242, and the second heat exchanger 26 is connected to the lubrication line 19 so that the water in the second water supply line 242 flowing from the water tank 22 cools the lubricating oil flowing to the compressor 11.

[0067] Based on the above-mentioned setting, the make-up water pipeline 24 is thermally coupled with the lubricating oil through the second heat exchanger 26 located on the second water supply pipeline 242 and the lubrication pipeline 19, so that the water provided by the make-up water system 2 can be cooled by exchanging heat with the lubricating oil flowing out of the oil tank 16 for cooling the compressor 11 at the second heat exchanger 26. In the corresponding process, since the make-up water can absorb the heat of the lubricating oil at the second heat exchanger 26 and reduce the temperature of the lubricating oil, the temperature of the lubricating oil flowing into the compressor 11 can be made lower, thereby achieving a better lubricating oil cooling effect and more effectively preventing the lubricating oil from overheating.

[0068] At the same time, the above solution achieves cooling of the lubricating oil by exchanging heat between the make-up water and the lubricating oil used to cool the compressor at the second heat exchanger 26. Since the make-up water does not need to be directly introduced into the oil tank 16, it can also prevent the quality of the lubricating oil from being affected by the make-up water entering the oil tank 16. In addition, the second heat exchanger 26 is also conducive to achieving more sufficient heat exchange between the lubricating oil and water.

[0069] It can be seen that by arranging a second heat exchanger 26 on the second water supply pipe 242 connected to the water tank 22, and connecting the second heat exchanger 26 to the lubrication pipe 19 for transporting the lubricating oil to the compressor 11, a safer and more efficient lubricating oil cooling process can be achieved, and the cooling effect of the lubricating oil can be effectively improved.

[0070] In the aforementioned embodiments, the water supply pipeline 24 may include only one of the first water supply pipeline 241 and the second water supply pipeline 242 , or may include both the first water supply pipeline 241 and the second water supply pipeline 242 .

[0071] In the case where the water supply pipeline 24 includes both the first water supply pipeline 241 and the second water supply pipeline 242, see Figure 1In some embodiments, the second water supply line 242 is connected to the portion of the first water supply line 241 between the first heat exchanger 25 and the water tank 22. In this case, the second water supply line 242 is not directly connected to the water tank 22, but rather is connected to the water tank 22 through the first water supply line 241. In this case, there is no need to equip the first and second water supply lines 241, 242 with separate make-up pumps 23. Instead, a single make-up pump 23 is required for the shared portion of the first and second water supply lines 241, 242. Furthermore, the number of valves can be reduced, thereby simplifying the structure and reducing costs. Furthermore, in this case, water flowing out of the water tank 22 can first flow into the first water supply line 241 and then be diverted to the first and second heat exchangers 25, 26, depending on the actual situation. This makes it easier to adjust the flow rate to the first and second heat exchangers 25, 26, thereby flexibly meeting the motor cooling, make-up water, and lubricant oil cooling requirements in different situations.

[0072] In the case where the second water supply line 242 is connected to the portion of the first water supply line 241 located between the first heat exchanger 25 and the water tank 22, see Figure 1 In some embodiments, the water replenishment system 2 further includes a second valve 28 , which is disposed at the connection between the first water supply pipeline 241 and the second water supply pipeline 242 , and controls the flow from the water tank 22 to the first heat exchanger 25 and the second heat exchanger 26 .

[0073] Since the second valve 28 can automatically adjust the distribution of water flowing out of the water tank 22 between the first heat exchanger 25 and the second heat exchanger 26, it is more convenient to achieve a timely and accurate flow distribution process and better meet different cooling needs. For example, it is convenient to adjust the opening of the second valve 28 according to the actual value of the lubricating oil temperature, increase or decrease the flow to the second heat exchanger 26, and adjust the temperature of the lubricating oil.

[0074] The water after cooling the lubricating oil can flow to the water replenishment port 124 to replenish the steam generator 12, or it can flow back to the water tank 22, or a part of it can flow to the water replenishment port 124 and the other part can flow back to the water tank 22. When the water replenishment pipeline 24 includes both the first water supply pipeline 241 and the second water supply pipeline 242, since the heat generated by the motor of the compressor 11 is usually high and the heat generated by the lubricating oil is low, the amount of water required for cooling the lubricating oil is small, and the temperature increase of the water by the lubricating oil is also small. Generally, the water flowing through the first heat exchanger 25 to cool the motor can meet the water replenishment demand. Therefore, in this case, only the water after cooling the motor can flow into the water replenishment port 124, and the water after cooling the lubricating oil can flow directly back to the water tank 22 without flowing to the water replenishment port 124. In this way, the pipeline connecting the second heat exchanger 26 to the water replenishment port 124 can be omitted, which is conducive to simplifying the structure.

[0075] In order to allow the water after cooling the lubricating oil to flow back to the water tank 22, see Figure 1 In some embodiments, the water supply line 24 includes not only a second water supply line 242 but also a second water return line 244. The second water return line 244 connects the second heat exchanger 26 and the water tank 22 to guide the water after cooling the lubricating oil back to the water tank 22. In this way, the water after cooling the lubricating oil can flow back to the water tank 22 via the second water return line 244, thereby reducing energy waste.

[0076] In the aforementioned embodiments, the steam generator 12 can adopt a structure in which the refrigerant flows through the shell side and the water flows through the tube side, or a structure in which the water flows through the shell side and the refrigerant flows through the tube side.

[0077] For example, see Figure 1 In some embodiments, the steam generator 12 includes a shell 121 and heat exchange tubes (not shown). The shell 121 is used to hold water, and a water supply port 124 is provided on the shell 121. The heat exchange tubes are connected to the shell 121 and to the discharge port 111 and throttle 13 of the compressor 11. This allows the high-temperature gaseous refrigerant discharged from the compressor 11 to flow into the heat exchange tubes, heating the water in the shell 121 into steam. In this case, the steam generator 12 adopts a shell-side water flow and tube-side refrigerant flow structure. In this case, the shell 121 can store steam, so that the steam generated by the steam generator 12 can be stored in the shell 121 and wait for use, without the need for additional components to store steam. Therefore, the structure is simpler.

[0078] In addition, in the aforementioned embodiments, the water supply pump 23 can be a fixed frequency pump or a variable frequency pump. When the water supply pump 23 is a fixed frequency pump, the structure is simpler, the control is more convenient, and it is easy to cooperate with the first valve 27 and / or the second valve 28 to achieve a more precise water supply and cooling process.

[0079] Based on the steam generating device 10 of the aforementioned embodiments, the present application further provides a control method, which includes:

[0080] Determine whether the steam generator 12 needs water replenishment;

[0081] When the steam generator 12 needs to be replenished with water, the water replenishment pipeline 24 is connected to the water replenishment port 124 of the steam generator 12 , and the water replenishment system 2 replenishes water for the steam generator 12 .

[0082] Based on the above steps, when steam generator 12 needs water replenishment, water replenishment system 2 can be used to replenish steam generator 12 and compensate for steam consumption. Because the water replenished by water replenishment system 2 to steam generator 12 has been preheated by at least one object to be cooled in heat pump system 1, it has a higher temperature and can be converted into steam at the required temperature more quickly and with less heat consumption, thereby improving steam production efficiency and energy efficiency. From another perspective, higher-temperature steam can be produced while consuming the same amount of heat, meeting the demand for higher-temperature steam from steam-consuming equipment.

[0083] Specifically, when the water supply line 24 includes the aforementioned first water supply line 241, connecting the water supply line 24 with the water supply port 124 of the steam generator 12 may include:

[0084] The first water supply pipe 241 of the water replenishment pipe 24 is connected to the water replenishment port 124 so that water flows through the first heat exchanger 25 on the first water supply pipe 241 in the process of flowing to the water replenishment port 124, and cools the refrigerant flowing from the refrigerant outlet 123 of the steam generator 12 to the motor of the compressor 11 at the first heat exchanger 25.

[0085] In this way, the make-up water can be used to cool the motor of the compressor 11, and while reducing the temperature of the compressor motor, the make-up water can be preheated, so that the water supplied to the steam generator 12 has a higher temperature, effectively improving the steam preparation efficiency and energy efficiency, and increasing the temperature of the prepared steam.

[0086] In the case where the first valve 27 is provided on the first water supply pipeline 241 , the connection and disconnection between the first water supply pipeline 241 and the water replenishment port 124 can be achieved by controlling the first valve 27 .

[0087] Additionally, in some embodiments, the control method includes:

[0088] After the heat pump system 1 receives the shutdown command, the water supply pipeline 24 is disconnected from the water supply port 124 after P minutes.

[0089] Based on the above steps, the water supply pipeline 24 is not disconnected from the water supply port 124 immediately after the heat pump system 1 receives the shutdown command, but is disconnected after a delay of P minutes. In this way, the water supply system 2 can still perform cooling and water supply work within P minutes after the heat pump system 1 is shut down, preventing the steam generator 12 from drying out and allowing the object to be cooled to cool quickly after the heat pump system 1 is shut down.

[0090] The value of P can be determined based on actual conditions. For example, in some embodiments, 1 ≤ P ≤ 5. In this case, the delayed disconnection time of the water supply line 24 is relatively appropriate, effectively preventing the steam generator 12 from drying out and allowing the object to be cooled to cool quickly after the heat pump system 1 is shut down, while also preventing unnecessary energy consumption due to excessively long delays.

[0091] As a further improvement to the above embodiments, the control method further includes:

[0092] The second valve 28 of the water supply system 2 is controlled to control the flow rate of water from the water tank 22 to the first heat exchanger 25 on the first water supply pipe 241 of the water supply pipe 24, for cooling the motor of the compressor 11, and the flow rate of water from the water tank 22 to the second heat exchanger 26 on the second water supply pipe 242 of the water supply pipe 24, for cooling the lubricating oil used to lubricate the compressor 11.

[0093] Controlling the second valve 28 can control the distribution of water flowing out of the water tank 22 between the first heat exchanger 25 and the second heat exchanger 26. This facilitates timely and accurate flow distribution and better meets different cooling needs. For example, it is convenient to adjust the opening of the second valve 28 according to the actual value of the lubricating oil temperature, increase or decrease the flow to the second heat exchanger 26, and adjust the temperature of the lubricating oil. It can be understood that the "flow rate flowing from the water tank 22 to the first heat exchanger 25 on the first water supply line 241 of the water supply line 24 to cool the motor of the compressor 11" specifically refers to "the flow rate of water flowing from the water tank 22 to the first heat exchanger 25 on the first water supply line 241 of the water supply line 24 to cool the refrigerant used to cool the motor of the compressor 11."

[0094] Specifically, in some embodiments, controlling the second valve 28 of the water replenishment system 2 includes:

[0095] The opening degree of the second valve 28 is controlled according to the oil supply temperature, wherein the oil supply temperature is the temperature of the lubricating oil flowing to the compressor 11 .

[0096] In the above steps, the oil supply temperature is used as the basis for adjusting the opening of the second valve, so that the opening of the second valve 28 matches the actual oil supply temperature, thereby realizing a dynamic water replenishment cooling process that better meets actual needs.

[0097] More specifically, in some embodiments, controlling the opening of the second valve 28 according to the oil supply temperature includes:

[0098] According to the oil supply temperature, determine the D value to determine the action range |D|%;

[0099] The opening degree of the second valve 28 is controlled according to the determined D value.

[0100] In the above steps, the action amplitude |D|% is determined according to the oil supply temperature, and the opening of the second valve 28 is adjusted according to the D value of the action amplitude |D|%. This makes it easier to accurately adjust the opening of the second valve 28, which is conducive to achieving a more accurate and efficient water replenishment cooling adjustment process.

[0101] Furthermore, in some embodiments, determining the D value according to the oil supply temperature includes:

[0102] When the actual value of the oil supply temperature is greater than or equal to the preset temperature, D=a*ΔT1+b*ΔT2; and / or,

[0103] When the actual value of the oil supply temperature is lower than the preset temperature, D = c*ΔT1;

[0104] Where ΔT1 = actual oil supply temperature - set oil supply temperature, ΔT2 = actual feed water temperature - set feed water temperature, a + b = 1, a ≥ b. Since the actual feed water temperature is usually lower than the set feed water temperature, ΔT2 is usually less than 0.

[0105] In the above steps, different formulas are used to calculate the D value according to the size relationship between the actual value of the oil supply temperature and the preset temperature value, which is conducive to calculating a D value that is more in line with actual needs. When adjusting the opening of the second valve 28, it can be adjusted according to the action amplitude |D|% that is more in line with actual needs, thereby realizing an opening adjustment process that is more in line with actual needs.

[0106] When the actual oil supply temperature is lower than the preset temperature, it indicates that the lubricating oil temperature is too low and the second valve 28 is already open widely. In this case, the lubricating oil viscosity is poor, the oil supply resistance increases, and the oil supply volume decreases, which easily triggers the oil pressure differential shutdown protection. Therefore, it is necessary to quickly close the second valve 28. To address this issue, the formula for calculating the D value when the actual oil supply temperature is lower than the preset temperature is constructed as D = c * Δt1. When the actual oil supply temperature is lower than the preset temperature, the opening adjustment range of the second valve 28 only considers the oil supply temperature, without considering the water supply temperature. This facilitates the rapid closing of the second valve 28, adjusting the lubricating oil temperature to a level greater than or equal to the preset temperature, and promoting the prompt release of the oil pressure differential shutdown protection.

[0107] When the actual oil supply temperature is greater than or equal to the preset temperature, it indicates that the temperature of the lubricating oil is relatively high. In this case, it is not easy to trigger the oil pressure difference shutdown protection, and the opening adjustment process of the second valve 28 (corresponding to the cooling process of the lubricating oil) can withstand a certain range. Regarding this characteristic, the calculation formula for D when the actual oil supply temperature is greater than or equal to the preset temperature is constructed as D = a*Δt1 + b*ΔT2, so that when the actual oil supply temperature is greater than or equal to the preset temperature, the opening adjustment range of the second valve 28 not only considers the oil supply temperature but also takes into account the water replenishment temperature, realizing the correction of the D value calculated according to the oil supply temperature by the water replenishment temperature. In this way, it is convenient to effectively reduce the temperature of the lubricating oil while taking into account the increase in the water replenishment temperature, making the lubricating oil cooling, motor cooling, and water replenishment preheating effects all better.

[0108] In the above formula, a, b, and c are all coefficients, which can be specifically set according to the actual situation. As an example, 0.5 ≤ a < 1, such as 0.6, 0.7, 0.8, or 0.9; and / or, 0 < b ≤ 0.5, such as 0.1, 0.2, 0.3, or 0.4; and / or, 0.5 ≤ c ≤ 1, such as 0.6, 0.7, 0.8, or 0.9. In this way, the magnitudes of a, b, and c are relatively appropriate, which is conducive to determining a D value that better meets the actual requirements and realizing a more accurate and efficient water replenishment cooling adjustment process.

[0109] In addition, the preset temperature can also be set according to the actual situation. As an example, in some embodiments, the preset temperature is 30 - 40 °C, such as 31 °C, 32 °C, 33 °C, 35 °C, 36 °C, 37 °C, 38 °C, or 39 °C. At this time, the magnitude of the preset temperature is relatively appropriate, and it is more suitable as a sign of whether the lubricating oil temperature is too low, which is convenient for determining different D values according to whether the lubricating oil temperature is too low and controlling the opening of the second valve 28 with different action amplitudes.

[0110] In some embodiments, controlling the opening of the second valve 28 according to the determined D value includes at least one of the following:

[0111] When D > m, increase the opening of the second valve 28 by |D|%;

[0112] When D < -m, decrease the opening of the second valve 28 by |D|%;

[0113] When -m ≤ D ≤ m, keep the opening of the second valve 28 unchanged;

[0114] Where m > 0.

[0115] In the above steps, m and -m are used as the dividing lines for whether the opening of the second valve 28 increases, decreases, or remains unchanged, so that the opening of the second valve 28 can remain unchanged within a certain range. In this way, the operating frequency of the second valve 28 can be reduced, and the second valve 28 can be prevented from moving back and forth, which affects its service life.

[0116] The value of m can be set according to actual conditions. For example, in some embodiments, 0.4≤m≤0.6, for example, 0.45, 0.5, or 0.55. In this way, the value of m is relatively appropriate and has a relatively small impact on the temperature. Therefore, it is more convenient to prevent the second valve 28 from moving back and forth without excessively affecting the temperature.

[0117] In the aforementioned embodiment for controlling the second valve 28, |D|% can be less than or equal to 3%, that is, |D|% ≤ 3%. Based on this, when adjusting the opening of the second valve 28, the operating amplitude is limited to a maximum opening, so that the operating amplitude |D|% does not exceed 3%. This prevents over-adjustment. In particular, after each operation, the temperature typically reacts slowly and there is a delay. In this case, limiting the operating amplitude |D|% to no more than 3% can effectively prevent over-adjustment caused by delayed temperature response. It can be understood that limiting the operating amplitude |D|% to no more than 3% means that if the calculated D value makes |D|% ≥ 3%, the adjustment is based on |D|% = 3%.

[0118] In addition, in some embodiments, when controlling the opening of the second valve 28 based on the oil supply temperature, the opening of the second valve 28 is controlled based on the oil supply temperature at predetermined intervals. This reduces the frequency of adjustments and controls, which not only helps prevent the second valve 28 from oscillating and affecting its lifespan, but also simplifies the control process and reduces costs.

[0119] The preset time can be set based on actual conditions. For example, in some embodiments, the preset time is 5 to 10 seconds, such as 6, 7, 8, or 9 seconds. In this case, the preset time is appropriate, the actuation frequency is more appropriate, and this helps extend the life of the second valve 28, simplify the control process, and reduce costs.

[0120] In some embodiments, when controlling the second valve 28 of the water replenishing system 2, the opening degree of the second valve 28 is made greater than or equal to a preset minimum opening degree A and less than or equal to a preset maximum opening degree B, where B > A. In this way, the maximum and minimum limits of the opening degree of the second valve 28 during the regulation process can be restricted, so that during the entire regulation process, the opening degree of the second valve 28 will not be too small, so as to avoid too small flow rate flowing to the second heat exchanger 26 and affecting the cooling of the lubricating oil. Moreover, the opening degree of the second valve 28 will not be too large, so as to avoid too small flow rate flowing to the first heat exchanger 25 and affecting water replenishment and motor cooling. That is to say, it can effectively meet the lubricating oil cooling requirements while taking into account water replenishment and motor cooling.

[0121] Among them, the values of A and B can be set according to the actual situation. For example, in some embodiments, 10% ≤ A < 20%, and / or, 10% < B ≤ 20%. At this time, the sizes of A and B are more appropriate, which is conducive to controlling the opening degree of the second valve 28 within a more appropriate range, and better taking into account water replenishment and motor cooling while effectively meeting the lubricating oil cooling requirements.

[0122] In addition, in some embodiments, controlling the second valve 28 of the water replenishing system 2 includes:

[0123] Before controlling the opening degree of the second valve 28 according to the oil supply temperature, first make the opening degree of the second valve 28 reach the preset minimum opening degree A and keep it for t minutes.

[0124] Based on the above steps, after receiving the startup command, the opening degree of the second valve 28 can be increased from 0% to the preset minimum opening degree A first and last for t minutes. Then, according to the oil supply temperature, the opening degree of the second valve 28 is controlled. This means that after startup, the opening degree of the second valve 28 is quickly increased to the preset minimum opening degree A. In this way, the basic cooling of the lubricating oil can be quickly achieved, preventing the lubricating oil from overheating in the initial stage of startup. And it also means that the regulation process of the opening degree of the second valve according to the oil supply temperature occurs after the opening degree of the second valve is not lower than the preset minimum opening degree A. Since in the corresponding situation, the detected oil supply temperature is more accurate, it is more conducive to realizing an accurate opening degree adjustment process.

[0125] Among them, the size of t can be set according to the actual situation. Exemplarily, 1 ≤ t ≤ 5. For example, it is 2, 3, or 4. At this time, the size of t is more appropriate, which is convenient for the regulation process of the opening degree of the second valve according to the oil supply temperature to occur after the basic cooling of the lubricating oil is guaranteed, and can also prevent the opening degree of the second valve 28 from not being adjusted according to the oil supply temperature for too long after startup, affecting the further cooling of the lubricating oil.

[0126] Furthermore, in some embodiments, after the heat pump system 1 receives a power-on command, the make-up water pump 23 is first turned on, and the compressor 11 is then turned on T1 minute after the make-up water pump 23 has been turned on. In this case, the compressor 11 is turned on only after the make-up water pump 23 has been turned on for T1 minute and no problems have occurred. This prevents damage to the compressor 11, and even to the entire heat pump system 1, caused by the compressor 11 being turned on in the event of a fault in the make-up water pump 23.

[0127] The value of T1 can be set according to actual conditions. In some embodiments, 1 ≤ T1 ≤ 5, for example, 2, 3, or 4. In this case, the delayed start time of compressor 11 is relatively appropriate, which can prevent compressor 11 from starting in the event of a water supply pump 23 failure and prevent the water supply pump 23 from operating too long before the compressor 11 starts, causing energy waste and other problems.

[0128] In addition, in some embodiments, the water supply pump 23 is turned off T2 minutes after the heat pump system 1 is shut down. In this case, the water supply pump 23 is turned off T2 minutes after the heat pump system 1 is shut down. This allows the water supply pump 23 to continue to supply water to the steam generator 12 for T2 minutes after the heat pump system 1 is shut down, effectively preventing dry burning in the steam generator 12.

[0129] The value of T2 can be set according to actual conditions. In some embodiments, 1≤T2≤5, for example, 2, 3, or 4. In this case, the delayed shutdown time of the water supply pump 23 is relatively appropriate, which can prevent dry burning in the steam generator 12 and prevent the water supply pump 23 from operating for too long after the heat pump system 1 is shut down, causing energy waste and other problems.

[0130] In addition, in some embodiments, when the water temperature in the water tank 22 is higher than the water tank temperature setting value, water is added to the water tank 22. In this way, by adding new water to the water tank 22, the water temperature in the water tank 22 can be lowered so that the water temperature in the water tank 22 can be lowered below the water tank temperature setting value, thereby preventing the water temperature in the water tank 22 from being too high and affecting the cooling effect on the motor and lubricating oil to be cooled.

[0131] Furthermore, in some embodiments, when the water temperature in the water tank 22 is higher than the set temperature value of the water tank 22 and the water level in the water tank 22 is lower than the upper water level limit, not only water is added to the water tank 22, but also water is drained from the water tank 22. In this way, during the process of replenishing water and adjusting the water temperature in the water tank, drainage can effectively prevent the water level in the water tank 22 from exceeding the upper water level limit, thereby improving the safety of the water tank water replenishment and temperature reduction process.

[0132] Specifically, in some embodiments, during the process of draining the water tank 22, if the water temperature in the water tank 22 is lower than the water tank temperature setting value by n°C, the water tank 22 is stopped from draining. In this way, the water temperature in the water tank 22 can be prevented from being too low.

[0133] The value of n can be set according to actual conditions. For example, in some embodiments, 2≤n≤5. In this case, the value of n is more appropriate, and the water temperature in the water tank 22 can be controlled within a more appropriate range.

[0134] In addition, in some embodiments, the control method further includes: stopping draining from the water tank 22 after the heat pump system 1 is shut down for T3 minutes. In this way, the water tank 22 can be delayed for T3 minutes before stopping draining after the heat pump system 1 is shut down. In this way, the water temperature and water level in the water tank 22 can be adjusted within T3 minutes after the heat pump system 1 is shut down, meeting the water replenishment and cooling needs of the heat pump system 1, preventing the steam generator 12 from drying out, and quickly cooling the object to be cooled.

[0135] The value of T3 can be set according to actual conditions. In some embodiments, 1≤T3≤5, for example, 2, 3, or 4. In this case, the water tank 22 delays shutting down and draining water for an appropriate time, which can prevent dry burning in the steam generator 12 and quickly cool the object to be cooled, while also preventing excessive draining time after shutdown, which could waste energy and other issues.

[0136] The control methods of the aforementioned embodiments can be performed under the control of a controller. Therefore, the present application also provides a controller comprising a memory and a processor coupled to the memory, wherein the processor is configured to execute the control method of any embodiment based on instructions stored in the memory.

[0137] Furthermore, the present application also provides a steam generating system, which includes the steam generating device of any embodiment and the controller of any embodiment.

[0138] In addition, the present application also provides a storage medium, which stores computer instructions, and the computer instructions are executed by a processor to implement the control method of any embodiment.

[0139] Next, combine Figure 1 The embodiments described above further introduce the present application.

[0140] like Figure 1 As shown, in this embodiment, the steam generating device 10 includes a heat pump system 1 , a water replenishment system 2 , a first temperature measuring component 3 , a second temperature measuring component 4 and a third temperature measuring component 5 .

[0141] The heat pump system 1 includes a compressor 11, a steam generator 12, a throttle 13, an evaporator 14, an oil tank 16, and an oil pump 17. The compressor 11, the steam generator 12, the throttle 13, and the evaporator 14 are sequentially connected to form a refrigerant circulation loop 15 for circulating refrigerant.

[0142] The steam generator 12 includes a shell 121 and heat exchange tubes (not shown). Shell 121 is used to hold water and is equipped with a refrigerant inlet 122, a refrigerant outlet 123, a water replenishment port 124, and an exhaust port 125. The refrigerant inlet 122 is connected to the discharge port 111 of the compressor 11, while the refrigerant outlet 123 is connected to the inlet 112 of the compressor 11 via a throttle 13. The heat exchange tubes are arranged on the side of the shell 121 and communicate with the refrigerant inlet 122 and the refrigerant outlet 123. This connects the heat exchange tubes to the discharge port 111 of the compressor 11 and the throttle 13. During operation, the high-temperature gaseous refrigerant discharged from the compressor 11 flows into the heat exchange tubes, heating the water in the shell 121 into steam. This achieves a steam generation method in which water flows in the shell side and refrigerant flows in the tube side. The generated steam is discharged through the exhaust port 125 for use by steam-consuming devices. A pressure regulating valve 127 is provided at the exhaust port 125 to regulate the steam exhaust pressure. The water replenishment port 124 is connected to the water replenishment system 2 to replenish water into the shell 11 of the steam generator 12 to compensate for steam consumption. A liquid level gauge 126 is provided within the steam generator 12 to monitor the liquid level within the steam generator 12 and facilitate water replenishment control.

[0143] In this embodiment, the refrigerant outlet 123 is also thermally coupled to the motor of the compressor 11 through the cooling pipe 18, so that the refrigerant flowing out of the steam generator 12 can flow to the motor of the compressor 11 to cool the motor of the compressor 11.

[0144] Furthermore, oil tank 16 contains lubricating oil and is connected to compressor 11 via lubrication line 19. Oil pump 17 supplies lubricating oil to compressor 11 to lubricate components within compressor 11. Lubrication line 19 is provided with a second temperature measuring element 4 to detect the temperature of the lubricating oil flowing into compressor 11.

[0145] In this embodiment, the lubricating oil and the motor of the compressor 11 constitute two objects to be cooled.

[0146] The water supply system 2 includes a one-way valve 20 , a water treatment device 21 , a water tank 22 , a water supply pump 23 , a water supply pipeline 24 , a first heat exchanger 25 , a second heat exchanger 26 , a first valve 27 , a second valve 28 and a drain valve 29 .

[0147] The water treatment device 21 is connected to the municipal water source and the water tank 22 to soften the municipal water and send the softened water to the water tank 22 .

[0148] The water tank 22 stores soft water and is connected to the water supply port 124 through the water supply pipe 24 to supply water to the steam generator 12 .

[0149] The drain valve 29 and the third temperature measuring component 5 are both provided on the water tank 22 , and are used to control whether the water tank 22 is drained and detect the water temperature in the water tank 22 , respectively.

[0150] The water supply line 24 connects the water tank 22 and the water supply port 124, and is thermally coupled to the motor of the compressor 11 and the lubricating oil through the first heat exchanger 25 and the second heat exchanger 26 to cool the lubricating oil and the motor of the compressor 11, and replenishes the water after cooling the motor of the compressor 11 into the steam generator 12. Figure 1 As shown, in this embodiment, the water supply pipeline 24 includes a first water supply pipeline 241, a second water supply pipeline 242, a first return water pipeline 243, and a second return water pipeline 244. The first water supply pipeline 241 connects the water tank 22 and the water supply port 124. A water supply pump 23, a second valve 28, a first heat exchanger 25, a first temperature measuring element 3, a first valve 27, and a one-way valve 20 are arranged on the first water supply pipeline 241 in the direction of water flow. The first heat exchanger 25 is a plate heat exchanger and is also connected to the cooling pipeline 18. The first temperature measuring element 3 detects the temperature of the water flowing out of the first heat exchanger 25. The first return water pipeline 243 connects the first valve 27 and the water tank 22. The second water supply pipeline 242 is connected to the second valve 28. The second heat exchanger 26 is a plate heat exchanger, which is arranged on the second water supply pipeline 242 and connected to the portion of the lubrication pipeline 19 located between the second temperature measuring component 4 and the oil pump 17 , and is connected to the water tank 22 through the second return water pipeline 244 .

[0151] As can be seen, in this embodiment, the heat pump system 1 integrates its own steam generator 12, which replaces the condenser of a conventional heat pump unit. The system uses high-temperature, high-pressure refrigerant in the tube side, while external make-up water is used in the shell side. The make-up water is heated by the refrigerant in the tube side and then flash-evaporates directly in the shell side. Because the unit integrates the steam generator 12, there is no need for a flash tank or circulating pump. This significantly increases the level of integration and provides significant cost advantages, effectively resolving the problem of heat pumps producing only hot water but no steam.

[0152] The consumed steam is replenished with softened make-up water after engineering treatment. The make-up water first cools the motor and lubricating oil of the unit's compressor 11 while preheating itself. The softened water that cooled the motor then enters the steam generator 12 to complete the make-up water. This effectively solves the problem of compressor 11's motor and lubricating oil being cooled only by refrigerant and constrained by evaporation temperature. It also effectively increases the temperature of the make-up water entering the steam generator 12, effectively cooling the motor and lubricating oil of compressor 11 while improving steam production efficiency and energy efficiency, and raising the temperature of the produced steam.

[0153] The steam generating device 10 of this embodiment works as follows:

[0154] The compressor 11 absorbs the gaseous refrigerant from the evaporator 14. The corresponding gaseous refrigerant is compressed by the compressor 11 and becomes a high-temperature and high-pressure gaseous refrigerant. It enters the heat exchange tube of the steam generator 12 through the refrigerant inlet 122 of the steam generator 12, is condensed into a high-pressure liquid refrigerant by the shell-side make-up water, and is then discharged through the refrigerant outlet 123. After being throttled by the throttling device 13, it enters the evaporator 14. In the corresponding process, water flows from the shell side of the steam generator 12, is heated by the high-temperature and high-pressure refrigerant on the tube side, and becomes high-temperature water. At the same time, high-temperature steam is flashed out. When the steam pressure in the steam generator 12 reaches the opening pressure of the pressure regulating valve 127, the pressure regulating valve 127 automatically opens to provide steam for steam-consuming equipment, and the consumed steam amount is supplemented by the softened water entering through the water supply port 124.

[0155] The softened water used for water replenishment is provided by the water replenishment system 2. During operation, municipal water enters the water treatment device 21 and is softened. The softened water then enters the water tank 22. The water replenishment pump 23 draws the softened water from the water tank 22 into the water replenishment pipeline 24 and is divided into two paths at the second valve 28. One path enters the second heat exchanger 26 and fully exchanges heat with the lubricating oil flowing from the oil tank 16 to the compressor 11. The softened water after cooling the lubricating oil returns to the water tank 22. After the lubricating oil cools down, it enters the compressor 11 to lubricate bearings and other components, and then returns to the oil tank 16; and the other path after passing through the second valve 28 enters the second heat exchanger 26. A heat exchanger 25 supercools the high-temperature and high-pressure liquid refrigerant from the refrigerant outlet 123 of the steam generator 12. The supercooled liquid refrigerant then passes through the bottom stop valve of the compressor 11 for throttling and pressure reduction and enters the motor winding cooling channel to cool the motor winding to prevent the motor from overheating and demagnetization. At the same time, the softened water absorbs the heat of the liquid refrigerant and is preheated, which greatly improves the system energy efficiency. The preheated softened water is divided into two paths through the first valve 27. One path enters the water supply port 124 through the one-way valve 20, and the other path returns to the water tank 22.

[0156] To meet the water supply demand of the steam generator 12 and the cooling demand of the motor and lubricating oil, and to increase the preheating temperature of the water supply, in this embodiment, the water supply pump 23, the first valve 27, the second valve 28, and the drain valve 29 are controlled as follows:

[0157] (1) Control method of water supply pump 23

[0158] The water supply pump 23 is a fixed frequency pump and adopts a control mode of early opening and delayed closing.

[0159] Specifically, when heat pump system 1 receives a power-on command, make-up water pump 23 starts 1-5 minutes before compressor 11. Once make-up water pump 23 is fault-free, compressor 11 is restarted. Make-up water pump 23 remains on during power-on operation. After heat pump system 1 shuts down, make-up water pump 23 delays shutting down for 1-5 minutes to prevent dry-burning in steam generator 12.

[0160] (2) Control method of the first valve 27

[0161] The first valve 27 is an electric three-way valve. When the outlet of the first valve 27 connected to the water supply port 124 is fully opened and the outlet connected to the water tank 22 is fully closed, the replenishment water will all flow to the water supply port 124.

[0162] When the heat pump unit is shut down, the opening of first valve 27 (specifically, the opening of the outlet of first valve 27 connected to water supply port 124) is 0%. Upon receiving a start-up command, the opening of first valve 27 is automatically controlled based on the liquid level in steam generator 12, as detected by liquid level gauge 126. It automatically opens wider when the liquid level falls below a preset level and closes narrower when the liquid level rises above the preset level. The opening is adjustable within a range of 0 to 100%. The control variable for the opening of first valve 27 only involves the liquid level. Many established control methods exist, and we will not elaborate on them here.

[0163] When the unit receives the shutdown command, the target opening of the first valve 27 is continuously controlled according to the preset liquid level, and is closed to 0% opening after 1 to 5 minutes, and the water supply pipeline 24 is disconnected from the water supply port 124 to stop water supply.

[0164] (2) Control method of the second valve 28

[0165] The second valve 28 is an electrically operated three-way valve. Its opening (specifically, the opening of the outlet of the second valve 28 connected to the second heat exchanger 26) is limited by a preset minimum opening A and a preset maximum opening B. After the system is operating stably, it is controlled by the oil supply temperature and the water supply temperature, and the action amplitude |D|% of each opening adjustment is subject to a maximum amplitude limit.

[0166] Specifically, when the outlet of second valve 28 connected to second heat exchanger 26 is fully open and the outlet connected to first heat exchanger 25 is fully closed, the makeup water will all flow to the lubricating oil side, cooling the lubricating oil. Therefore, when heat pump system 1 is turned on, while cooling the lubricating oil, to meet the makeup water flow and motor cooling requirements, the maximum opening of second valve 28 is limited to B. That is, the maximum opening is preset to B to meet the makeup water flow and motor cooling requirements, and the minimum opening of second valve 28 is limited to A. That is, the minimum opening is preset to A to meet the lubricating oil cooling requirements. Wherein, B>A, and B and A range from 10% to 20%.

[0167] When the heat pump system 1 is in shutdown state, the target opening of the second valve 28 is 0%. After the unit receives the startup command, the target opening of the second valve 28 increases from 0% to A and lasts for 1 to 5 minutes.

[0168] After 1 to 5 minutes, the second valve 28 enters the automatic adjustment mode. During the startup operation, the opening degree is between A and B. In the automatic adjustment mode, the second valve 28 is controlled by the oil supply temperature and the water supply temperature (i.e., the temperature of the water flowing to the water supply port 124). It performs an action every 5 to 10 seconds, and the amplitude of each action |D|% does not exceed 3% (if it exceeds 3%, it will be calculated as 3%).

[0169] In automatic adjustment mode, the parameters used are:

[0170] Oil supply temperature difference ΔT1 = oil supply temperature - oil supply temperature setting value; and

[0171] Make-up water temperature difference ΔT2 = make-up water temperature - make-up water temperature setting value.

[0172] When the oil supply temperature T1 ≥ 35°C, the calculation formula for the D value of the action amplitude |D|% is D = 0.7*ΔT1 + 0.3*ΔT2; and when the oil supply temperature T1 < 35°C, the calculation formula for the D value of |D|% is D = 0.8*ΔT1.

[0173] According to the different D values ​​obtained by calculation, different control strategies are adopted as follows:

[0174] When D>0.5, the opening of the second valve 28 increases by |D|%;

[0175] When 0.5 ≥ D ≥ -0.5, the opening of the second valve 28 remains unchanged;

[0176] When D<-0.5, the opening degree of the second valve 28 is reduced by |D|%.

[0177] Since D=0.5 has little effect on the temperature, the above control strategy is adopted to maintain the temperature when the amplitude is small and open or close the temperature accordingly when the amplitude is large, so as to prevent the second valve 28 from moving back and forth, so as to avoid affecting the life of the second valve 28 due to repeated back and forth movements.

[0178] When the unit receives the shutdown command, the opening of the second valve 28 changes from the current opening to 0%, and the use of softened water to cool the lubricating oil stops.

[0179] (4) Control method of drain valve 29

[0180] The drain valve 29 is a solenoid valve, and its opening and closing are related to the water tank water replenishment operation. When the drain valve 29 is opened and the water tank is drained, water is replenished to the water tank 22.

[0181] When the heat pump system is shut down, the drain valve 29 remains closed.

[0182] After receiving the power-on command, the heat pump system 1 detects the water temperature in the water tank 22 in real time. When the water temperature in the water tank 22 is higher than the water tank temperature setting value, the drain valve 29 is opened and water is replenished; when the water temperature in the water tank 22 is 2 to 5°C lower than the water tank temperature setting value, the drain valve 29 is closed.

[0183] After the heat pump system 1 receives the shutdown command, the drain valve 29 continues to be controlled according to the set value of the water tank temperature, and after 1 to 5 minutes, the drain valve 29 is closed.

[0184] The water replenishment of the water tank 22 is controlled by the engineering. When the water level in the water tank is lower than the lower water level limit, or the water level in the water tank is lower than the upper water level limit and the drain valve 29 is open, water is automatically replenished into the water tank 22 when one of the two conditions is met. When the water level reaches the upper water level limit, the water replenishment is stopped.

[0185] It can be seen that in this embodiment, the heat pump system 1 can directly flash steam while generating hot water, without the need for a flash tank and a circulating water supply pump. It has a simple structure and can directly replace the boiler. In addition, the motor and lubricating oil of the heat pump system 1 are waiting for the cooling of the cooling object, and the water supply can be directly used as a cold source. The cooling effect is no longer limited by the evaporation temperature. At the same time, the heat generated by the unit's own motor can preheat the water supply, and the water supply can be converted into steam after preheating to greatly improve energy efficiency. Moreover, a fixed-frequency water supply pump + an electric three-way water valve is used, and combined with a liquid level meter, a temperature measuring component, a heat exchanger, and a drain valve, in conjunction with the unit controller, the cooling of each object to be cooled in the unit and the water supply flow and water supply preheating temperature required after steam generation can be accurately controlled, thereby achieving efficient and reliable operation of the steam generating equipment 10.

[0186] This embodiment is only described by taking the heat pump system 1 including a one-stage compressor as an example. However, it should be noted that, depending on the difference between the heat source temperature and the output temperature, the compressor 11 is not limited to single-stage compression, but can be two-stage compression, or three-stage or four-stage compression with two compressors 11 connected in series. Depending on the number of compression stages, corresponding cooling motor flow paths (i.e., cooling pipelines 18) and cooling lubricating oil flow paths (i.e., second water supply pipelines 242) can be set. For example, if two compressors 11 are connected in series, the supercooled refrigerant of the cooling motor can be divided into two cooling motors, and at the same time, the water replenishment is divided into two cooling lubricating oils.

[0187] The above description is merely an exemplary embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A steam generating device (10), characterized in that: include: A heat pump system (1) comprises a compressor (11), a steam generator (12), a throttling element (13) and an evaporator (14), wherein the compressor (11), the steam generator (12), the throttling element (13) and the evaporator (14) are sequentially connected to form a refrigerant circulation loop (15) for circulating a refrigerant, the steam generator (12) utilizes the refrigerant to heat water into steam, and the steam generator (12) has a water supply port (124); and A water supply system (2) comprises a water tank (22), a water supply pump (23) and a water supply pipeline (24); the water supply pipeline (24) is connected to the water tank (22) and the water supply port (124), and is thermally coupled to at least one object to be cooled of the heat pump system (1); the water supply pump (23) is arranged on the water supply pipeline (24) to drive the water in the water tank (22) to directly or indirectly cool the at least one object to be cooled, and drives the water after cooling the at least one object to be cooled to flow to the water supply port (124) to supply water to the steam generator (12).

2. The steam generating device (10) according to claim 1, characterized in that The at least one object to be cooled includes a motor of the compressor (11); the refrigerant outlet (123) of the steam generator (12) is thermally coupled to the motor through a cooling pipe (18) so as to cool the motor using the refrigerant flowing out of the steam generator (12); the water supply pipe (24) includes a first water supply pipe (241); the first water supply pipe (241) is connected to the water tank (22) and the water supply port (124); a first heat exchanger (25) is provided on the first water supply pipe (241); the first heat exchanger (25) is connected to the cooling pipe (18) so that the water in the water tank (22) flows through the first heat exchanger (25) in the process of flowing to the water supply port (124), and cools the refrigerant flowing from the refrigerant outlet (123) to the motor at the first heat exchanger (25).

3. The steam generating device (10) according to claim 2, characterized in that The water replenishment pipeline (24) further comprises a first water return pipeline (243), the first water return pipeline (243) being connected to the water tank (22) and to a portion of the first water supply pipeline (241) located between the first heat exchanger (25) and the water replenishment port (124) so ​​as to guide water flowing out of the first heat exchanger (25) back to the water tank (22).

4. The steam generating device (10) according to claim 3, characterized in that The water replenishment system (2) further comprises a first valve (27), which is arranged at the connection between the first return water pipeline (243) and the first water supply pipeline (241) to control the flow of water from the first heat exchanger (25) to the water replenishment port (124) and the first return water pipeline (243).

5. The steam generating device (10) according to any one of claims 1 to 4, characterized in that: The heat pump system (1) includes an oil tank (16), the oil tank (16) is connected to the compressor (11) through a lubricating pipeline (19) to supply lubricating oil to the compressor (11) to lubricate the compressor (11), the at least one object to be cooled includes the lubricating oil, the water supply pipeline (24) includes a second water supply pipeline (242), the second water supply pipeline (242) is connected to the water tank (22), a second heat exchanger (26) is provided on the second water supply pipeline (242), and the second heat exchanger (26) is connected to the lubricating pipeline (19) so that the water flowing from the water tank (22) into the second water supply pipeline (242) cools the lubricating oil flowing to the compressor (11).

6. The steam generating device (10) according to claim 5, characterized in that The second water supply pipeline (242) is connected to the portion of the first water supply pipeline (241) of the water supply pipeline (24) located between the first heat exchanger (25) and the water tank (22).

7. The steam generating device (10) according to claim 6, characterized in that The water replenishment system (2) further comprises a second valve (28), which is arranged at the connection between the first water supply pipeline (241) and the second water supply pipeline (242) and controls the flow rate from the water tank (22) to the first heat exchanger (25) and the second heat exchanger (26).

8. The steam generating device (10) according to claim 5, characterized in that The water supply pipeline (24) further includes a second water return pipeline (244), which connects the second heat exchanger (26) and the water tank (22) to guide the water after cooling the lubricating oil back to the water tank (22).

9. The steam generating device (10) according to any one of claims 1 to 4, characterized in that: The steam generator (12) includes a shell (121) and a heat exchange tube. The shell (121) is used to contain water. The water supply port (124) is provided on the shell (121). The heat exchange tube is connected to the shell (121) and is connected to the outlet (111) of the compressor (11) and the throttling element (13) so that the high-temperature gaseous refrigerant discharged from the compressor (11) flows into the heat exchange tube and heats the water in the shell (121) into steam.

10. The steam generating device (10) according to any one of claims 1 to 4, characterized in that: The water replenishment pump (23) is a fixed frequency pump.

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