Cold source device, dual-cold source hot and cold water unit, and control method

Abstract

The present invention provides a cold source device, a dual-cold source cold and hot water unit, and a control method, relating to the technical field of refrigeration equipment. The cold source device includes a first heat exchanger, a second heat exchanger, an evaporative condensing module, and a spray device. The evaporative condensing module includes a water pump and a first fan, a spray device, a cooling packing, and a water storage device arranged from top to bottom. The first heat exchanger is disposed between the spray device and the cooling packing, and the spray device is connected to the water storage device. The second heat exchanger is disposed above the water storage device and spaced apart from the first heat exchanger. The spray device is connected to the water pump via a second conduit and is used to spray water onto the second heat exchanger. The present invention also provides a dual-cold source cold and hot water unit that utilizes the cold source device described above. The present invention also provides a control method applicable to the dual-cold source cold and hot water unit described above. The cold source device, dual-cold source cold and hot water unit, and control method provided by the present invention can improve heat exchange efficiency, thereby enhancing energy efficiency.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration equipment, and in particular to a cold source device, a dual-cold source hot and cold water unit, and a control method. Background Art

[0002] With the advancement of technology, many large-scale evaporative cooling units have been put into use. However, most cooling modes currently operate independently, using water cooling, air cooling, and evaporative cooling. Air cooling offers high condensing temperatures and low energy consumption in the summer, while evaporative cooling is prone to icing when used for heating in the winter. Furthermore, the heat exchange efficiency of most existing evaporative cooling units is low, resulting in ineffective energy efficiency improvements. Summary of the Invention

[0003] The objects of the present invention include, for example, providing a cold source device that can improve heat exchange efficiency and thus improve energy efficiency.

[0004] The present invention also aims to provide a dual-cold source hot and cold water unit, which can improve heat exchange efficiency and thus improve energy efficiency.

[0005] Another object of the present invention is to provide a control method for a dual-cold-source hot and cold water unit, which can improve energy efficiency.

[0006] The embodiments of the present invention can be implemented as follows:

[0007] An embodiment of the present invention provides a cold source device, comprising a first heat exchanger, a second heat exchanger, an evaporative condensing module, and a spray device.

[0008] The evaporative condensing module includes a water pump and a first fan, a spray device, a cooling packing, and a water storage device arranged from top to bottom. The first heat exchanger is disposed between the spray device and the cooling packing. The spray device is connected to the water storage device via a first conduit. The water pump is mounted on the first conduit to direct water from the water storage device to the spray device. The spray device is used to spray water onto the first heat exchanger.

[0009] The second heat exchanger is arranged above the water storage device and is spaced apart from the first heat exchanger. The spray device is connected to the water pump through a second conduit. The water pump is also used to introduce water in the water storage device into the spray device. The spray device is used to spray water to the second heat exchanger.

[0010] The beneficial effects of the cold source device provided by the present invention compared with the prior art include: the cold source device can drain the water in the water storage device and spray the water on the second heat exchanger through the spray device. During summer cooling, the outdoor air can exchange heat with the low-temperature water when the air enters, which can reduce the dry-bulb temperature of the incoming air, which is beneficial to reducing the condensing temperature of the refrigeration system, increasing the heat exchange capacity of the refrigeration system and reducing energy consumption, thereby achieving the purpose of improving energy efficiency.

[0011] Optionally, the spray device includes a first nozzle and a second nozzle, both of which are connected to the water pump through the second conduit, the first nozzle is arranged near the top of the second heat exchanger and is used to spray water toward the top of the second heat exchanger, and the second nozzle is arranged near the bottom of the second heat exchanger and is used to spray water toward the bottom of the second heat exchanger.

[0012] Optionally, a first solenoid valve is provided on the second conduit, and the first solenoid valve is used to selectively open or close the second conduit.

[0013] Optionally, the second heat exchanger is arranged in a V shape.

[0014] Optionally, the cold source device further includes a second fan, which is arranged on the top of the second heat exchanger and is used to guide the airflow from the second heat exchanger to the second fan.

[0015] A dual-cold-source hot and cold water unit includes a compressor, a four-way valve, an expansion valve, a heat exchanger, and a cold source device. The cold source device includes a first heat exchanger, a second heat exchanger, an evaporative condensing module, and a spray device.

[0016] The evaporative condensing module includes a water pump and a first fan, a spray device, a cooling packing, and a water storage device arranged from top to bottom. The first heat exchanger is disposed between the spray device and the cooling packing. The spray device is connected to the water storage device via a first conduit. The water pump is mounted on the first conduit to direct water from the water storage device to the spray device. The spray device is used to spray water onto the first heat exchanger.

[0017] The second heat exchanger is arranged above the water storage device and is spaced apart from the first heat exchanger. The spray device is connected to the water pump through a second conduit. The water pump is also used to introduce water in the water storage device into the spray device. The spray device is used to spray water to the second heat exchanger.

[0018] The first heat exchanger and the second heat exchanger are arranged in parallel to form a cooling passage.

[0019] The four-way valve has a first port, a second port, a third port and a fourth port.

[0020] The liquid outlet of the compressor is connected to the first interface, and the liquid inlet of the compressor is connected to the second interface.

[0021] One end of the heat exchanger is connected to the third interface, and the other end of the heat exchanger is connected to the expansion valve.

[0022] One end of the cooling passage is connected to the expansion valve, and the other end of the cooling passage is connected to the fourth interface.

[0023] The dual-cold source hot and cold water unit provided by the present invention has the following beneficial effects compared with the prior art: when cooling in the summer, the outdoor air can exchange heat with low-temperature water when the air enters, which can reduce the dry-bulb temperature of the incoming air, which is beneficial to reducing the condensing temperature of the refrigeration system, increasing the heat exchange capacity of the refrigeration system and reducing energy consumption, thereby achieving the purpose of improving energy efficiency.

[0024] Optionally, the cooling passage includes a first channel, a second channel, a first heat exchanger, and a second heat exchanger. The first channel includes a third conduit and a fourth conduit, the third conduit and the fourth conduit are respectively connected to two ends of the first heat exchanger, the second heat exchanger is connected to the second channel, the other end of the third conduit is connected to one end of the second channel, and the other end of the fourth conduit is connected to the other end of the second channel.

[0025] Optionally, a seventh conduit is provided between the expansion valve and the heat exchanger, and the dual-cold-source hot and cold water unit further includes a fifth conduit and a sixth conduit.

[0026] The third conduit is provided with a second electromagnetic valve, and one end of the fifth conduit is connected between the second electromagnetic valve and the first heat exchanger.

[0027] The fourth conduit is provided with a third solenoid valve, and one end of the sixth conduit is connected between the third solenoid valve and the first heat exchanger.

[0028] The fifth conduit is provided with a fourth solenoid valve, and the sixth conduit is provided with a fifth solenoid valve.

[0029] A sixth solenoid valve is provided on the seventh conduit, and the sixth solenoid valve is located between the expansion valve and the heat exchanger. The other end of the fifth conduit is connected between the sixth solenoid valve and the heat exchanger, and the other end of the sixth conduit is connected between the sixth solenoid valve and the expansion valve.

[0030] Furthermore, when the dual-cold source hot and cold water unit is in a low-temperature environment, by closing the third solenoid valve, the second solenoid valve and the sixth solenoid valve, the evaporative condensing module acts as a supercooler, using the heat of the refrigerant to heat the water in the water storage device, and then directing the water in the water storage device to the spray device to spray the high-temperature water on the second heat exchanger, which can prevent the second heat exchanger from frosting, thereby ensuring that the second heat exchanger can effectively exchange heat and achieve the purpose of improving energy efficiency.

[0031] A control method is applied to the above dual-cold-source hot and cold water unit, the control method comprising:

[0032] According to a first control signal issued when the dual-cold-source hot and cold water unit operates in a cooling mode, the water pump, the first solenoid valve, the third solenoid valve, the second solenoid valve, and the sixth solenoid valve are all controlled to be open, the fourth solenoid valve and the fifth solenoid valve are controlled to be closed, and the second fan is controlled to operate at a first preset speed;

[0033] receiving a first cooling water temperature value and an exhaust pressure value, wherein the first cooling water temperature value represents the water temperature in the water storage device, and the exhaust pressure value represents the exhaust pressure of the compressor;

[0034] Determining whether the startup and operation time of the dual-cold-source hot and cold water unit reaches a first preset time;

[0035] If yes, adjusting the operating frequency of the first fan according to the exhaust pressure value, a first preset pressure value, and a second preset pressure value, wherein the first preset pressure value is greater than the second preset pressure value;

[0036] If not, the first fan is controlled to operate according to the first cooling water temperature value and the preset water temperature value.

[0037] Optionally, the step of adjusting the operating frequency of the first fan according to the exhaust pressure value, the first preset pressure value, and the second preset pressure value includes:

[0038] When the exhaust pressure value is greater than the first preset pressure value, controlling the operating frequency of the first fan to increase by a preset frequency every preset period until the operating frequency of the first fan reaches a maximum operating frequency;

[0039] When the exhaust pressure value is less than or equal to the first preset pressure value and greater than or equal to the second preset pressure value, controlling the first fan to maintain the current operating frequency;

[0040] When the exhaust pressure value is less than the second preset pressure value, the operating frequency of the first fan is controlled to decrease by a preset frequency every preset period until the operating frequency of the first fan reaches a minimum operating frequency.

[0041] Optionally, the step of controlling the operation of the first fan according to the first cooling water temperature value and the preset water temperature value includes:

[0042] When the first cooling water temperature value is lower than the preset water temperature value for a second preset time, turning off the first fan;

[0043] When the first cooling water temperature is greater than or equal to the preset water temperature, the first fan is controlled to operate at a preset operating frequency.

[0044] A control method is applied to the above dual-cold-source hot and cold water unit, the control method comprising:

[0045] receiving an ambient temperature value and an evaporation pressure value according to a second control signal issued when the dual-cold-source cold and hot water unit operates in a hot water mode, wherein the ambient temperature value represents the temperature of the environment in which the dual-cold-source cold and hot water unit is located, and the evaporation pressure value represents the evaporation pressure of the refrigerant in the first heat exchanger;

[0046] Determining whether the ambient temperature value is greater than a preset outer ring temperature value;

[0047] If not, when the ambient temperature value is less than or equal to the preset outer ring temperature value for a third preset time, controlling the water pump, the first solenoid valve, the fourth solenoid valve, and the fifth solenoid valve to be turned on, and controlling the third solenoid valve, the second solenoid valve, the sixth solenoid valve, and the second fan to be turned off;

[0048] If so, the water pump, the second solenoid valve, the third solenoid valve and the sixth solenoid valve are controlled to open, the first solenoid valve, the fourth solenoid valve and the fifth solenoid valve are controlled to close, the second fan is controlled to run at a second preset speed, and the first fan is controlled to run at a preset operating frequency; and the operating frequency of the first fan is adjusted according to the evaporation pressure value, the third preset pressure value and the fourth preset pressure value, wherein the third preset pressure value is greater than the fourth preset pressure value.

[0049] Optionally, the step of adjusting the operating frequency of the first fan according to the evaporation pressure value, the third preset pressure value, and the fourth preset pressure value includes:

[0050] When the evaporation pressure value is greater than a third preset pressure value, controlling the operating frequency of the first fan to increase by a preset frequency every preset period until the operating frequency of the first fan reaches a maximum operating frequency;

[0051] When the evaporation pressure value is less than or equal to the third preset pressure value and greater than or equal to the fourth preset pressure value, controlling the first fan to maintain the current operating frequency;

[0052] When the evaporation pressure value is less than the fourth preset pressure value, the operating frequency of the first fan is controlled to decrease by a preset frequency every preset period until the operating frequency of the first fan reaches a minimum operating frequency.

[0053] The control method of the embodiment of the present invention is applied to the above-mentioned dual-cold source hot and cold water unit, and the beneficial effects of the control method relative to the prior art are the same as the beneficial effects of the above-mentioned dual-cold source hot and cold water unit relative to the prior art, which will not be repeated here. BRIEF DESCRIPTION OF THE DRAWINGS

[0054] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments. It should be understood that the following drawings only illustrate certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without paying any creative work.

[0055] Figure 1 This is a schematic structural diagram of a dual-cold source hot and cold water unit provided in an embodiment of the present application;

[0056] Figure 2 This is a schematic structural diagram of a cooling source device provided in an embodiment of the present application;

[0057] Figure 3 This is a flow chart of a control method provided in an embodiment of the present application;

[0058] Figure 4 This is a specific flow chart of step S14 in a control method provided in an embodiment of the present application;

[0059] Figure 5 This is a specific flow chart of step S15 in a control method provided in an embodiment of the present application;

[0060] Figure 6 A specific flow chart of another control method provided in an embodiment of the present application;

[0061] Figure 7 This is a specific flow chart of step S24 in another control method provided in an embodiment of the present application.

[0062] Icons: 10-dual-cold-source hot and cold water unit; 100-cold source device; 110-evaporative condensing module; 111-first fan; 112-spray device; 113-cooling filler; 114-water storage device; 115-water pump; 120-first heat exchanger; 130-second heat exchanger; 131-second fan; 140-spray device; 141-first nozzle; 142-second nozzle; 210-compressor; 220-four-way valve; 230-heat exchanger ;240-expansion valve;310-first conduit;320-second conduit;321-first solenoid valve;330-third conduit;331-second solenoid valve;340-fourth conduit;341-third solenoid valve;350-fifth conduit;351-fourth solenoid valve;360-sixth conduit;361-fifth solenoid valve;370-seventh conduit;371-sixth solenoid valve;410-cooling passage;411-first channel;412-second channel. DETAILED DESCRIPTION

[0063] To make the objectives, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions of the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings herein can be arranged and designed in various different configurations.

[0064] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention as claimed, but rather merely represents selected embodiments of the present invention. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without creative effort shall fall within the scope of protection of the present invention.

[0065] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined or explained in subsequent drawings.

[0066] In the description of the present invention, it should be noted that if the terms "upper", "lower", "inside", "outside", etc. appear, the orientation or position relationship indicated is based on the orientation or position relationship shown in the accompanying drawings, or is the orientation or position relationship in which the product of the invention is usually placed when in use. It is only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be understood as a limitation on the present invention.

[0067] In addition, the terms "first", "second", etc., if used, are merely used to distinguish and describe, and should not be understood as indicating or implying relative importance.

[0068] It should be noted that, in the absence of conflict, the features in the embodiments of the present invention may be combined with each other.

[0069] See also Figure 1 In one embodiment of the present application, a dual-cold-source hot and cold water unit 10 is provided. This dual-cold-source hot and cold water unit 10 can be used to provide cooling or heating, thereby adjusting the air quality in a designated area to meet the needs of users in that area. Of course, this dual-cold-source hot and cold water unit 10 can also provide hot water to users, further meeting their needs. Furthermore, this dual-cold-source hot and cold water unit 10 can improve heat exchange efficiency, thereby increasing energy efficiency.

[0070] The dual-cold-source cold and hot water unit 10 includes a cold source device 100, a four-way valve 220, a compressor 210, a heat exchanger 230, and an expansion valve 240. The cold source device 100, the four-way valve 220, the compressor 210, the heat exchanger 230, and the expansion valve 240 are interconnected to form a circuit. The compressor 210 compresses the refrigerant to provide high-temperature, high-pressure refrigerant within the circuit and also provides power for the refrigerant to circulate within the circuit. The heat exchanger 230 outputs cooling or heating to a designated area, thereby regulating the air quality in that area. The expansion valve 240 reduces the pressure and temperature of the refrigerant. The cold source device 100 allows the refrigerant to pass through and provides a space for heat exchange between the refrigerant and the external environment. In the embodiments of the present application, the cold source device 100 can improve heat exchange efficiency, thereby enhancing energy efficiency, thereby enabling the dual-cold-source cold and hot water unit 10 to achieve improved heat exchange efficiency and energy efficiency.

[0071] Please refer to Figure 1 and Figure 2 The cold source device 100 includes a first heat exchanger 120 , a second heat exchanger 130 , an evaporative condensing module 110 and a spray device 140 .

[0072] The evaporative condensing module 110 includes a water pump 115, a first fan 111, a spray device 112, a cooling packing 113, and a water storage device 114 arranged from top to bottom. A first heat exchanger 120 is located between the spray device 112 and the cooling packing 113. The spray device 112 is connected to the water storage device 114 via a first conduit 310. The water pump 115 is mounted on the first conduit 310 and directs water from the water storage device 114 to the spray device 112. The spray device 112 sprays the water onto the first heat exchanger 120, thereby exchanging heat with the water sprayed onto the first heat exchanger 120 as the refrigerant passes through the first heat exchanger 120. The first fan 111 directs airflow through the first heat exchanger 120, causing the water on the first heat exchanger 120 to evaporate. This facilitates the absorption of heat from the refrigerant in the first heat exchanger 120, enhancing the cooling effect on the refrigerant. In addition, the first heat exchanger 120 can also be used to heat water sprayed onto the first heat exchanger 120. The water on the first heat exchanger 120 can drip into the water storage device 114 after being collected.

[0073] The second heat exchanger 130 is disposed above the water storage device 114, and is spaced apart from the first heat exchanger 120 to prevent mutual interference between the first and second heat exchangers 120, 130, and to facilitate installation of the first and second heat exchangers 120, 130. It should be noted that the water storage device 114 can be a long water tank, so that the first and second heat exchangers 120, 130 can be spaced apart above the water storage device 114. Of course, the water storage device 114 can also be two spaced-apart water tanks, with the first and second heat exchangers 120, 130 respectively disposed above the two water tanks, which are interconnected by a conduit to facilitate water flow between the two water tanks. In addition, the spray device 140 is connected to the water pump 115 through the second conduit 320. After the water pump 115 pumps out the water in the water storage device 114, it can guide the water to the spray device 140 through the second conduit 320. The spray device 140 is arranged close to the second heat exchanger 130, and the spray device 140 is used to spray water onto the second heat exchanger 130.

[0074] As described above, when cooling in high-temperature environments such as summer, the outdoor air can exchange heat with the low-temperature water upon entering the airflow, which can lower the dry-bulb temperature of the incoming air, thereby lowering the condensing temperature of the refrigeration system, increasing the heat exchange capacity of the refrigeration system, and reducing energy consumption, thereby achieving the purpose of improving energy efficiency. In addition, in low-temperature environments such as winter, the spray device 140 can spray high-temperature water onto the second heat exchanger 130 to reduce frost on the second heat exchanger 130, thereby improving the heat exchange efficiency of the second heat exchanger 130 and further improving the energy efficiency of the dual-cold-source hot and cold water unit 10.

[0075] In an embodiment of the present application, in order to further improve the heat exchange efficiency of the second heat exchanger 130, the spray device 140 includes a first nozzle 141 and a second nozzle 142. The first nozzle 141 and the second nozzle 142 are both connected to the water pump 115 through the second conduit 320. That is, the first nozzle 141 and the second nozzle 142 can be regarded as being arranged in parallel. The water drawn out from the water pump 115 is partially directed to the first nozzle 141 and partially directed to the second nozzle 142, so that the first nozzle 141 and the second nozzle 142 can spray at the same time. In addition, the first nozzle 141 is arranged near the top of the second heat exchanger 130 and is used to spray water to the top of the second heat exchanger 130; the second nozzle 142 is arranged near the bottom of the second heat exchanger 130 and is used to spray water to the bottom of the second heat exchanger 130. It should be noted that the spraying direction of the first nozzle 141 is toward the second heat exchanger 130, that is, the second nozzle 142 sprays water from the top of the second heat exchanger 130 toward the bottom of the second heat exchanger 130; and the spraying direction of the second nozzle 142 is toward the second heat exchanger 130, that is, the first nozzle 141 sprays water from the bottom of the second heat exchanger 130 toward the top of the second heat exchanger 130. By respectively arranging the first nozzle 141 and the second nozzle 142 at the top and bottom of the second heat exchanger 130, a comprehensive spraying effect can be provided to the second heat exchanger 130, thereby comprehensively improving the heat exchange efficiency of the second heat exchanger 130 and avoiding the problem of uneven heat exchange caused by localized heat exchange efficiency increases, thereby effectively improving energy efficiency.

[0076] In addition, in the embodiment of the present application, a first solenoid valve 321 is provided on the second conduit 320. The first solenoid valve 321 is used to selectively open or close the second conduit 320. When the first solenoid valve 321 closes the second conduit 320, the spray device 140 does not operate. When the first solenoid valve 321 opens the second conduit 320, the water pump 115 can direct water to the spray device 140.

[0077] In the embodiment of the present application, the second heat exchanger 130 is arranged in a V-shape. In other words, the second heat exchanger 130 can be regarded as comprising a first heat exchange zone (not marked in the figure) and a second heat exchange zone (not marked in the figure). The first heat exchange zone and the second heat exchange zone are both arranged in a flat plate shape by coils. An angle is formed between the flat plate structure formed by the first heat exchange zone and the flat plate structure formed by the second heat exchange zone, so that the entire second heat exchanger 130 forms a V-shaped structure. Figure 2For example, in an embodiment of the present application, when the cooling source device 100 is properly positioned, the opening of the V-shaped structure formed by the second heat exchanger 130 faces upward. Accordingly, the first nozzle 141 disposed near the top of the second heat exchanger 130 corresponds to the portion where the first and second heat exchange zones are separated from each other; the second nozzle 142 disposed near the bottom of the second heat exchanger 130 corresponds to the portion where the second and first heat exchange zones connect.

[0078] In addition, in an embodiment of the present application, the cold source device 100 may further include a second fan 131, which is disposed on top of the second heat exchanger 130 and is configured to guide airflow from the second heat exchanger 130 to the second fan 131. In other words, the second fan 131 is configured to guide airflow from the bottom of the second heat exchanger 130 toward the top of the second heat exchanger 130.

[0079] In the dual-cold-source hot and cold water unit 10 provided herein, a first heat exchanger 120 and a second heat exchanger 130 are connected in parallel to form a cooling passage 410. A four-way valve 220 has a first port, a second port, a third port, and a fourth port. The liquid outlet of the compressor 210 is connected to the first port, and the liquid inlet of the compressor 210 is connected to the second port. One end of the heat exchanger 230 is connected to the third port, and the other end is connected to the expansion valve 240. One end of the cooling passage 410 is connected to the expansion valve 240, and the other end of the cooling passage 410 is connected to the fourth port. The four-way valve 220 can be used to selectively connect the first interface and the fourth interface and the second interface and the third interface. At this time, the dual-cold source hot and cold water unit 10 is in the cooling mode. The high-temperature and high-pressure refrigerant discharged by the compressor 210 is guided to the cooling path 410 through the four-way valve 220. After being cooled by the first heat exchanger 120 and the second heat exchanger 130, the refrigerant is guided in sequence through the expansion valve 240 and the heat exchanger 230 and then returns to the four-way valve 220. It returns to the compressor 210 under the guidance of the second interface. Alternatively, the first interface and the third interface are connected and the second interface and the fourth interface are connected. At this time, the dual-cold-source hot and cold water unit 10 is in hot water mode. The high-temperature and high-pressure refrigerant discharged by the compressor 210 is guided to the heat exchanger 230 through the four-way valve 220, and can provide heat to the user or heat the user's water to provide hot water to the user; after passing through the heat exchanger 230, the refrigerant can return to the four-way valve 220 through the expansion valve 240 and the cooling passage 410 respectively, and return to the compressor 210 under the guidance of the second interface.

[0080] Furthermore, in an embodiment of the present application, the cooling passage 410 includes a first channel 411, a first channel 411, a first heat exchanger 120, and a second heat exchanger 130. The first channel 411 includes a third conduit 330 and a fourth conduit 340. The third conduit 330 and the fourth conduit 340 are respectively connected to the two ends of the first heat exchanger 120, and the second heat exchanger 130 is connected to the second channel 412. The other end of the third conduit 330 is connected to one end of the second channel 412, and the other end of the fourth conduit 340 is connected to the other end of the second channel 412, so that the first channel 411 and the second channel 412 are arranged in parallel to form the cooling passage 410.

[0081] Furthermore, to facilitate control of the dual-cold-source cold and hot water unit 10 and thereby improve its energy efficiency, in the embodiment of the present application, the expansion valve 240 and the heat exchanger 230 are connected via a seventh conduit 370. The dual-cold-source cold and hot water unit 10 may also include a fifth conduit 350 and a sixth conduit 360. Furthermore, a second solenoid valve 331 is provided on the third conduit 330, which is configured to selectively open or close the third conduit 330. One end of the fifth conduit 350 is connected to the third conduit 330 between the second solenoid valve 331 and the first heat exchanger 120. A third solenoid valve 341 is provided on the fourth conduit 340, which is configured to selectively open or close the fourth conduit 340. One end of the sixth conduit 360 is connected to the fourth conduit 340 between the third solenoid valve 341 and the first heat exchanger 120. A sixth solenoid valve 371 is provided on the seventh conduit 370 and is located between the expansion valve 240 and the heat exchanger 230. The other end of the fifth conduit 350 is connected to the seventh conduit 370 between the sixth solenoid valve 371 and the heat exchanger 230. The other end of the sixth conduit 360 is connected to the seventh conduit 370 between the sixth solenoid valve 371 and the expansion valve 240. Furthermore, a fourth solenoid valve 351 is provided on the fifth conduit 350 and is used to selectively open or close the fifth conduit 350. A fifth solenoid valve 361 is provided on the sixth conduit 360 and is used to selectively open or close the sixth conduit 360.

[0082] It should be noted that in the embodiment of the present application, the dual-cold-source hot and cold water unit 10 may further include a controller, and the four-way valve 220, the first solenoid valve 321, the second solenoid valve 331, the third solenoid valve 341, the fourth solenoid valve 351, the fifth solenoid valve 361, and the sixth solenoid valve 371 are all electrically connected to the controller, so that the controller can control the switching state of the four-way valve 220 and the opening and closing states of the first solenoid valve 321, the second solenoid valve 331, the third solenoid valve 341, the fourth solenoid valve 351, the fifth solenoid valve 361, and the sixth solenoid valve 371. In addition, the controller may also be connected to the first fan 111, the second fan 131, and the water pump 115, and the controller may be used to control the operating frequency and on / off state of the first fan 111 and the second fan 131. The controller may also be used to control the on / off state of the water pump 115.

[0083] In addition, please refer to Figure 1 and Figure 3 In an embodiment of the present application, in order to improve the energy efficiency of the dual-cold-source hot and cold water unit 10 and to facilitate the control of the dual-cold-source hot and cold water unit 10, an embodiment of the present application further provides a control method. The control method is applied to the aforementioned dual-cold-source hot and cold water unit 10 and can achieve the purpose of improving the energy efficiency of the dual-cold-source hot and cold water unit 10. The control method includes:

[0084] Step S11: According to the first control signal issued when the dual-cold-source hot and cold water unit 10 operates in the cooling mode, the water pump 115, the first solenoid valve 321, the second solenoid valve 331, the third solenoid valve 341, and the sixth solenoid valve 371 are controlled to be open, and the fourth solenoid valve 351 and the fifth solenoid valve 361 are controlled to be closed, and the second fan 131 is controlled to operate at a first preset speed.

[0085] It should be noted that the controller controls the four-way valve 220 to connect the first and fourth interfaces, and the second and third interfaces. In cooling mode, the controller controls the water pump 115, the first solenoid valve 321, the third solenoid valve 341, and the sixth solenoid valve 371 to open, and controls the fourth solenoid valve 351 and the fifth solenoid valve 361 to close. In the circuit of the dual-cold-source hot and cold water unit 10, the refrigerant discharged from the compressor 210 enters the first interface and is directed to the cooling passage 410 via the fourth interface. Part of the refrigerant enters the first heat exchanger 120 via the third conduit 330, and part of the refrigerant enters the second heat exchanger 130 via the second passage 412. The refrigerant cooled in the first heat exchanger 120 is directed to the expansion valve 240 via the fourth conduit 340, and the refrigerant cooled in the second heat exchanger 130 is directed to the expansion valve 240 via the second passage 412. After the refrigerant has been reduced in pressure and temperature by the expansion valve 240, it is directed through the seventh conduit 370 to the heat exchanger 230, allowing the heat exchanger 230 to provide cooling to the outside. The refrigerant that has passed through the heat exchanger 230 enters the four-way valve 220 through the third interface and exits the four-way valve 220 through the second interface. The refrigerant then returns to the compressor 210, completing a refrigeration cycle. Furthermore, at this time, the second solenoid valve 331 is controlled to be conductive, and the second fan 131 is controlled to operate at the first preset speed. This allows the spray device 140 to spray water onto the second heat exchanger 130, while the second fan 131 guides the airflow through the second heat exchanger 130, thereby improving the heat exchange efficiency of the second heat exchanger 130. The first preset speed can be set to a lower speed to reduce energy consumption while ensuring that the second heat exchanger 130 can provide effective heat exchange.

[0086] Step S12: Receive a first cooling water temperature value and an exhaust pressure value.

[0087] The first cooling water temperature value represents the water temperature in the water storage device 114 , and the exhaust pressure value represents the exhaust pressure of the compressor 210 .

[0088] Step S13: determining whether the startup operation time of the dual-cold-source hot and cold water unit 10 reaches a first preset time.

[0089] That is, the controller can compare the startup and operation time of the dual-cold source hot and cold water unit 10 with the first preset time. When the startup and operation time of the dual-cold source hot and cold water unit 10 is greater than or equal to the first preset time, it means that the startup and operation time of the dual-cold source hot and cold water unit 10 reaches the first preset time.

[0090] Step S14: If yes, adjust the operating frequency of the first fan 111 according to the exhaust pressure value, the first preset pressure value and the second preset pressure value.

[0091] The first preset pressure value is greater than the second preset pressure value.

[0092] It should be noted that if the judgment in step S13 is yes, it indicates that the dual-source cold and hot water unit 10 has been running for a first predetermined time. At this point, the water temperature in the water storage device 114 of the dual-source cold and hot water unit 10 has increased, and the exhaust pressure of the compressor 210 has stabilized. At this point, the operating frequency of the first fan 111 can be adjusted based on the exhaust pressure of the compressor 210, thereby improving the heat exchange efficiency of the refrigerant in the cooling passage 410.

[0093] Optionally, see Figure 4 , step S14 may include:

[0094] Step S141 : When the exhaust pressure value is greater than a first preset pressure value, the operating frequency of the first fan 111 is controlled to increase by a preset frequency every preset period until the operating frequency of the first fan 111 reaches a maximum operating frequency.

[0095] Step S142: When the exhaust pressure value is less than or equal to the first preset pressure value and greater than or equal to the second preset pressure value, control the first fan 111 to maintain the current operating frequency.

[0096] Step S143 : When the exhaust pressure value is less than the second preset pressure value, the operating frequency of the first fan 111 is controlled to decrease by a preset frequency every preset period until the operating frequency of the first fan 111 reaches a minimum operating frequency.

[0097] It should be noted that the preset period can range from 0 to 60 seconds. In the embodiment of the present application, the preset period is 10 seconds. Of course, in other embodiments, the preset period can also be 5 seconds, 15 seconds, 20 seconds, 25 seconds, or 30 seconds. In addition, the first preset pressure value, the second preset pressure value, and the preset frequency can all be manually set by the operator.

[0098] In addition, in an embodiment of the present application, the exhaust pressure value of the compressor 210 is received and judged every preset period, and when the exhaust pressure value satisfies any of the conditions in step S141, step S142, or step S143, the operating frequency of the first fan 111 is adjusted. For example, when the exhaust pressure value is greater than the first preset pressure value, it indicates that the heat exchange efficiency provided in the cooling passage 410 is low. By increasing the operating frequency of the first fan 111, the heat exchange efficiency of the first heat exchanger 120 is increased, thereby improving the overall heat exchange efficiency of the dual-cold source hot and cold water unit 10, thereby achieving the purpose of improving energy efficiency. Of course, when the operating frequency of the first fan 111 reaches the maximum operating frequency, the maximum operating frequency can be maintained. In step S142, when the exhaust pressure value is between the first preset pressure value and the second preset pressure value, the first fan 111 is controlled to maintain the current operating frequency, which can also be regarded as controlling the first fan 111 to operate at the operating frequency of the previous cycle. In addition, there is no restriction on the order of step S141, step S142 and step S143, and the corresponding step can be executed if the conditions of any step are met. The first preset pressure value and the second preset pressure value can be set manually.

[0099] Step S15: If not, control the first fan 111 to operate according to the first cooling water temperature value and the preset water temperature value.

[0100] If the result of step S13 is negative, it indicates that the dual-cooling-source hot and cold water unit 10 has been operating for a short time, indicating that the water temperature in the water storage device 114 is relatively low. This means that the spray device 112 can provide better heat exchange efficiency between the first heat exchanger 120 and the refrigerant. This means that spraying water onto the first heat exchanger 120 and the second heat exchanger 130 through the spray device 112 can meet the refrigerant's heat exchange requirements. Furthermore, since the exhaust pressure of the compressor 210 is unstable at this time, the operation of the first fan 111 can be controlled solely based on the first cooling water temperature.

[0101] Optionally, see Figure 5 , step S15 may include:

[0102] Step S151 : when the first cooling water temperature is lower than the preset water temperature for a second preset time, turning off the first fan 111 .

[0103] Since the first cooling water temperature is lower than the preset water temperature, the water in water storage device 114 is sufficient to effectively exchange heat in first heat exchanger 120. Therefore, operation of first fan 111 is unnecessary to enhance the heat exchange efficiency of first heat exchanger 120, thereby reducing energy consumption. By determining whether the first cooling water temperature remains lower than the preset water temperature for a second preset time, misjudgments can be avoided and control accuracy can be ensured.

[0104] Step S152: When the first cooling water temperature is greater than or equal to a preset water temperature, control the first fan 111 to operate at a preset operating frequency.

[0105] If the first cooling water temperature is greater than or equal to the preset water temperature, it indicates that the heat exchange provided by the water in the water storage device 114 is insufficient to meet user needs. Therefore, the heat exchange efficiency provided by the first heat exchanger 120 to the refrigerant is improved by turning on the first fan 111 at a preset frequency, thereby ensuring that the dual-cooling source hot and cold water unit 10 can provide effective cooling. This improves energy efficiency and reduces energy consumption.

[0106] As described above, when the dual-cold-source hot and cold water unit 10 operates in cooling mode, the control method improves the heat exchange efficiency by setting a spray device 140 on the second heat exchanger 130, and controls the operating frequency of the first fan 111 according to the temperature of the water in the water storage device 114 and the exhaust temperature of the compressor 210, so as to further improve the heat exchange efficiency while reducing energy consumption, that is, to ensure that the overall dual-cold-source hot and cold water unit 10 can improve the heat exchange efficiency while reducing the energy consumption of the dual-cold-source hot and cold water unit 10.

[0107] In addition, please refer to Figure 1 and Figure 6 The dual-cold-source hot and cold water unit 10 can also be used to provide hot water and heat to users. That is, the dual-cold-source hot and cold water unit 10 can provide hot water and heat to users when operating in hot water mode. In order to improve the energy efficiency of the dual-cold-source hot and cold water unit 10 in hot water mode, another control method is provided in the embodiment of the present application. The control method includes:

[0108] Step S21: receiving an ambient temperature value and an evaporation pressure value according to a second control signal issued when the dual-cold-source hot and cold water unit 10 operates in a hot water mode.

[0109] The ambient temperature value represents the temperature of the environment in which the dual-cold-source hot and cold water unit 10 is located; and the evaporation pressure value represents the evaporation pressure of the refrigerant in the first heat exchanger 120 .

[0110] It should be noted that when operating in hot water mode, the controller controls four-way valve 220 to connect the first and third interfaces, and the second and fourth interfaces. At this time, the high-temperature, high-pressure refrigerant discharged from compressor 210 is directly introduced into heat exchanger 230, which provides heat or hot water to the user. The refrigerant discharged from heat exchanger 230 is cooled in cooling passage 410 and then returned to compressor 210 by four-way valve 220, completing the cycle.

[0111] Step S22: Determine whether the ambient temperature is greater than the preset outer ring temperature.

[0112] Step S23: If not, when the ambient temperature value is less than or equal to the preset outer ring temperature value for a third preset time, the water pump 115, the first solenoid valve 321, the fourth solenoid valve 351 and the fifth solenoid valve 361 are controlled to be open, and the third solenoid valve 341, the second solenoid valve 331, the sixth solenoid valve 371 and the second fan 131 are controlled to be closed.

[0113] At this time, after the refrigerant is discharged from the heat exchanger 230, it enters the fifth conduit 350 and, under the guidance of the fifth conduit 350, enters the third conduit 330. The third conduit 330 guides the refrigerant to the first heat exchanger 120 and then to the fourth conduit 340. The fourth conduit 340 guides the refrigerant to the sixth conduit 360. The sixth conduit 360 guides the refrigerant to the seventh conduit 370. The seventh conduit 370 guides the refrigerant to the expansion valve 240. The refrigerant passing through the expansion valve 240 enters the second channel 412. The refrigerant passing through the second heat exchanger 130 is guided back to the four-way valve 220 through the second channel 412 and then returns to the compressor 210, completing the cycle. However, since the external temperature is lower than the preset external temperature, frost may form on the second heat exchanger 130. At this time, because the high-temperature refrigerant first enters the first heat exchanger 120, the first heat exchanger 120 heats the collected water, which then falls into the water storage device 114. Therefore, the water in the water storage device 114 is at a high temperature. Therefore, spraying the water in the water storage device 114 onto the second heat exchanger 130 via the spray device 140 can reduce frost formation on the second heat exchanger 130, thereby improving the heat exchange efficiency of the second heat exchanger 130 and enhancing the energy efficiency of the dual-cold-source hot and cold water unit 10.

[0114] Step S24: If yes, control the water pump 115, the second solenoid valve 331, the third solenoid valve 341 and the sixth solenoid valve 371 to be opened, control the first solenoid valve 321, the fourth solenoid valve 351 and the fifth solenoid valve 361 to be closed, control the second fan 131 to operate at the second preset speed, and control the first fan 111 to operate at the preset operating frequency; and adjust the operating frequency of the first fan 111 according to the evaporation pressure value, the third preset pressure value and the fourth preset pressure value.

[0115] The third preset pressure value is greater than the fourth preset pressure value.

[0116] At this point, after the refrigerant is discharged from heat exchanger 230, it is introduced into seventh conduit 370, which directs part of the refrigerant to fourth conduit 340 and part of the refrigerant to second channel 412. The refrigerant entering fourth conduit 340 passes through first heat exchanger 120 and third conduit 330 in sequence before being directed to four-way valve 220. The refrigerant entering second channel 412 passes through second heat exchanger 130 and is directed to four-way valve 220. The refrigerant is then directed back to compressor 210 via the second port, completing a complete cycle. Due to the relatively high ambient temperature, frost is less likely to form on second heat exchanger 130 and first heat exchanger 120. Therefore, the first and second heat exchangers 120, 130, jointly provide heat exchange for the refrigerant, improving the refrigerant's heat exchange efficiency and thus the energy efficiency of the dual-cold-source refrigerant unit. In addition, the operating frequency of the first fan 111 can also be controlled by the evaporation pressure value of the first heat exchanger 120 to improve the heat exchange efficiency of the first heat exchanger 120, thereby improving the energy efficiency of the dual-cold source hot and cold water unit 10.

[0117] Optionally, see Figure 7 The step of adjusting the operating frequency of the first fan 111 according to the evaporation pressure value, the third preset pressure value and the fourth preset pressure value in step S24 may include:

[0118] Step S241 : When the evaporation pressure value is greater than a third preset pressure value, control the operating frequency of the first fan 111 to increase by a preset frequency every preset period until the operating frequency of the first fan 111 reaches a maximum operating frequency.

[0119] Step S242: When the evaporation pressure value is less than or equal to the third preset pressure value and greater than or equal to the fourth preset pressure value, control the first fan 111 to maintain the current operating frequency.

[0120] Step S243 : When the evaporation pressure value is less than the fourth preset pressure value, control the operating frequency of the first fan 111 to decrease by a preset frequency every preset period until the operating frequency of the first fan 111 reaches a minimum operating frequency.

[0121] It should be noted that the evaporation pressure of the refrigerant in the first heat exchanger 120 is received and determined during each preset cycle, and when the evaporation pressure value satisfies any of the conditions in step S241, step S242, or step S243, the operating frequency of the first fan 111 is adjusted. For example, when the evaporation pressure value is greater than the third preset pressure value, it indicates that the heat exchange effect provided by the first heat exchanger 120 is low. By increasing the operating frequency of the first fan 111, the heat exchange efficiency of the first heat exchanger 120 is increased, thereby improving the overall heat exchange efficiency of the dual-cold source hot and cold water unit 10, thereby achieving the purpose of improving energy efficiency. Of course, when the operating frequency of the first fan 111 reaches the maximum operating frequency, it is sufficient to maintain the maximum operating frequency. In step S242, when the evaporation pressure value is between the third preset pressure value and the fourth preset pressure value, the first fan 111 is notified to maintain the current operating frequency. This can also be regarded as controlling the first fan 111 to operate at the operating frequency of the previous cycle. In addition, there is no restriction on the order of step S241, step S242 and step S243. If the conditions of any step are met, the corresponding step can be executed.

[0122] In addition, the third preset pressure value and the fourth preset pressure value can be set manually.

[0123] As described above, the dual-cold-source cold and hot water unit 10 and its control method provided in the embodiments of the present application, when the dual-cold-source cold and hot water unit 10 is operating in hot water mode, controls the direction of refrigerant flow based on the temperature of the external environment, thereby improving frosting in low-temperature environments, while also improving the energy efficiency of the dual-cold-source cold and hot water unit 10 and reducing energy consumption. Furthermore, in high-temperature environments, the first heat exchanger 120 and the second heat exchanger 130 jointly provide heat exchange, thereby improving the energy efficiency of the dual-cold-source cold and hot water unit 10 and reducing energy consumption.

[0124] In summary, the cold source device 100, the dual cold source hot and cold water unit 10, and the control method provided in the embodiments of the present application can achieve the purpose of improving the overall heat exchange efficiency, thereby improving the overall energy efficiency, while also reducing energy consumption. Specifically, in a high temperature environment, the first heat exchanger 120 and the second heat exchanger 130 jointly provide a heat exchange effect to the refrigerant, and the through hole controls the operating frequency of the first fan 111 to further improve the heat exchange efficiency, thereby achieving the purpose of improving the overall energy efficiency, while also reducing energy consumption. In a low temperature environment, the frosting of the second heat exchanger 130 can be improved, while also improving the overall energy efficiency and reducing overall energy consumption.

[0125] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present invention should be included in the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be based on the scope of protection of the claims.

Claims

1. A dual-cold source hot and cold water unit, characterized in that: It includes a compressor (210), a four-way valve (220), an expansion valve (240), a heat exchanger (230), and a cold source device (100); The cold source device (100) comprises a first heat exchanger (120), a second heat exchanger (130), an evaporative condensation module (110), and a spray device (140); The evaporative condensing module (110) comprises a water pump (115) and a first fan (111), a spray device (112), a cooling filler (113) and a water storage device (114) arranged from top to bottom; the first heat exchanger (120) is arranged between the spray device (112) and the cooling filler (113); the spray device (112) is connected to the water storage device (114) through a first conduit (310), and the water pump (115) is installed on the first conduit (310) to guide water in the water storage device (114) into the spray device (112); the spray device (112) is used to spray water to the first heat exchanger (120); The second heat exchanger (130) is arranged above the water storage device (114) and is spaced apart from the first heat exchanger (120). The spray device (140) is connected to the water pump (115) through a second conduit (320). The water pump (115) is also used to guide water in the water storage device (114) into the spray device (140). The spray device (140) is used to spray water onto the second heat exchanger (130). The first heat exchanger (120) and the second heat exchanger (130) are arranged in parallel to form a cooling passage (410); The four-way valve (220) has a first interface, a second interface, a third interface and a fourth interface; The liquid outlet of the compressor (210) is connected to the first interface, and the liquid inlet of the compressor (210) is connected to the second interface; One end of the heat exchanger (230) is connected to the third interface, and the other end of the heat exchanger (230) is connected to the expansion valve (240); One end of the cooling passage (410) is connected to the expansion valve (240), and the other end of the cooling passage (410) is connected to the fourth interface; The cooling passage (410) comprises a first channel (411), a second channel (412), a first heat exchanger (120), and a second heat exchanger (130); the first channel (411) comprises a third conduit (330) and a fourth conduit (340); the third conduit (330) and the fourth conduit (340) are respectively connected to two ends of the first heat exchanger (120); the second heat exchanger (130) is connected to the second channel (412); the other end of the third conduit (330) is connected to one end of the second channel (412); and the other end of the fourth conduit (340) is connected to the other end of the second channel (412); A seventh conduit (370) is provided between the expansion valve (240) and the heat exchanger (230), and the dual-cold-source hot and cold water unit (10) further includes a fifth conduit (350) and a sixth conduit (360); A second electromagnetic valve (331) is provided on the third conduit (330), and one end of the fifth conduit (350) is connected between the second electromagnetic valve (331) and the first heat exchanger (120); A third electromagnetic valve (341) is provided on the fourth conduit (340), and one end of the sixth conduit (360) is connected between the third electromagnetic valve (341) and the first heat exchanger (120); The fifth conduit (350) is provided with a fourth solenoid valve (351), and the sixth conduit (360) is provided with a fifth solenoid valve (361); A sixth solenoid valve (371) is provided on the seventh conduit (370), and the sixth solenoid valve (371) is located between the expansion valve (240) and the heat exchanger (230). The other end of the fifth conduit (350) is connected between the sixth solenoid valve (371) and the heat exchanger (230), and the other end of the sixth conduit (360) is connected between the sixth solenoid valve (371) and the expansion valve (240).

2. The dual-cold source hot and cold water unit according to claim 1, characterized in that: The spray device (140) includes a first nozzle (141) and a second nozzle (142). The first nozzle (141) and the second nozzle (142) are both connected to the water pump (115) through the second conduit (320). The first nozzle (141) is arranged near the top of the second heat exchanger (130) and is used to spray water toward the top of the second heat exchanger (130). The second nozzle (142) is arranged near the bottom of the second heat exchanger (130) and is used to spray water toward the bottom of the second heat exchanger (130). A first solenoid valve (321) is arranged on the second conduit (320). The first solenoid valve (321) is used to selectively open or close the second conduit (320).

3. A control method, applied to the dual-cold-source hot and cold water unit (10) according to claim 1 or 2, wherein a first solenoid valve (321) is provided on the second conduit (320), and a second fan (131) is provided on the top of the second heat exchanger (130), characterized in that: The control method includes: According to a first control signal issued when the dual-cold-source hot and cold water unit (10) operates in a cooling mode, the water pump (115), the first solenoid valve (321), the third solenoid valve (341), the second solenoid valve (331), and the sixth solenoid valve (371) are all controlled to be open, and the fourth solenoid valve (351) and the fifth solenoid valve (361) are controlled to be closed, and the second fan (131) is controlled to operate at a first preset speed; receiving a first cooling water temperature value and an exhaust pressure value, wherein the first cooling water temperature value represents the water temperature in the water storage device (114), and the exhaust pressure value represents the exhaust pressure of the compressor (210); Determining whether the startup operation time of the dual-cold-source hot and cold water unit (10) has reached a first preset time; If yes, adjusting the operating frequency of the first fan (111) according to the exhaust pressure value, a first preset pressure value, and a second preset pressure value, wherein the first preset pressure value is greater than the second preset pressure value; If not, the first fan (111) is controlled to operate according to the first cooling water temperature value and the preset water temperature value.

4. The control method according to claim 3, characterized in that: The step of adjusting the operating frequency of the first fan (111) according to the exhaust pressure value, the first preset pressure value and the second preset pressure value comprises: When the exhaust pressure value is greater than the first preset pressure value, controlling the operating frequency of the first fan (111) to increase by a preset frequency every preset period until the operating frequency of the first fan (111) reaches a maximum operating frequency; When the exhaust pressure value is less than or equal to the first preset pressure value and greater than or equal to the second preset pressure value, controlling the first fan (111) to maintain the current operating frequency; When the exhaust pressure value is less than the second preset pressure value, the operating frequency of the first fan (111) is controlled to decrease by a preset frequency every preset period until the operating frequency of the first fan (111) reaches a minimum operating frequency.

5. The control method according to claim 3, characterized in that: The step of controlling the operation of the first fan (111) according to the first cooling water temperature value and the preset water temperature value comprises: When the first cooling water temperature value is lower than the preset water temperature value for a second preset time, turning off the first fan (111); When the first cooling water temperature value is greater than or equal to the preset water temperature value, the first fan (111) is controlled to operate at a preset operating frequency.

6. A control method, applied to the dual-cold-source hot and cold water unit (10) according to claim 1 or 2, wherein a first solenoid valve (321) is provided on the second conduit (320), and a second fan (131) is provided on the top of the second heat exchanger (130), characterized in that: The control method includes: receiving an ambient temperature value and an evaporation pressure value according to a second control signal issued when the dual-cold-source cold and hot water unit (10) operates in a hot water mode, wherein the ambient temperature value represents the temperature of the environment in which the dual-cold-source cold and hot water unit (10) is located, and the evaporation pressure value represents the evaporation pressure of the refrigerant in the first heat exchanger (120); Determining whether the ambient temperature value is greater than a preset outer ring temperature value; If not, when the ambient temperature value is less than or equal to the preset outer ring temperature value for a third preset time, the water pump (115), the first solenoid valve (321), the fourth solenoid valve (351) and the fifth solenoid valve (361) are controlled to be open, and the third solenoid valve (341), the second solenoid valve (331), the sixth solenoid valve (371) and the second fan (131) are controlled to be closed; If so, the water pump (115), the second solenoid valve (331), the third solenoid valve (341) and the sixth solenoid valve (371) are controlled to be opened, the first solenoid valve (321), the fourth solenoid valve (351) and the fifth solenoid valve (361) are controlled to be closed, the second fan (131) is controlled to operate at a second preset speed, and the first fan (111) is controlled to operate at a preset operating frequency; and the operating frequency of the first fan (111) is adjusted according to the evaporation pressure value, the third preset pressure value and the fourth preset pressure value, wherein the third preset pressure value is greater than the fourth preset pressure value.

7. The control method according to claim 6, characterized in that: The step of adjusting the operating frequency of the first fan (111) according to the evaporation pressure value, the third preset pressure value and the fourth preset pressure value comprises: When the evaporation pressure value is greater than a third preset pressure value, controlling the operating frequency of the first fan (111) to increase by a preset frequency every preset period until the operating frequency of the first fan (111) reaches a maximum operating frequency; When the evaporation pressure value is less than or equal to a third preset pressure value and greater than or equal to a fourth preset pressure value, controlling the first fan (111) to maintain the current operating frequency; When the evaporation pressure value is less than the fourth preset pressure value, the operating frequency of the first fan (111) is controlled to decrease by a preset frequency every preset period until the operating frequency of the first fan (111) reaches a minimum operating frequency.

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