A dynamically controllable dual evaporator system

Abstract

The utility model discloses a kind of dual-evaporator systems of dynamic control, including throttling element A, evaporator A, electronic control valve A, electronic control valve B, solenoid valve C, throttling element C, evaporator C and check valve C, they constitute the refrigerant parallel structure with three branches, wherein by throttling element A, evaporator A, electronic control valve A form first branch, by electronic control valve B form second branch, by solenoid valve C, throttling element C, evaporator C and check valve C form third branch.The utility model utilizes the switch and proportional adjustment of 2 electronic control valves, realize the control of different evaporation pressure and evaporation temperature, simultaneously solve the evaporation overheating problem generated due to load or environmental temperature change.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration systems, specifically a dynamically controllable dual evaporator system. Background Technology

[0002] With the rapid development of electronic devices and equipment, people have increasingly higher demands for traditional compressor refrigeration. These demands include air conditioning systems with two different temperature compartments, refrigerant systems with two different liquid supply temperatures, and composite refrigeration systems with one liquid cooling path and one air cooling path, all with temperature control capabilities. The traditional approach is to use two independent compressor refrigeration systems, each controlling either the liquid or air supply. However, this approach is sometimes unsuitable due to limitations in space and reliability.

[0003] In the cooling fields of lasers, radar, and other high-energy conversion applications, various types of refrigerant systems are increasingly emerging. These systems provide all-weather temperature protection for the heat load by supplying coolant, and also require air conditioning to control the temperature and humidity of the cabin environment. This necessitates at least one refrigerant system and one air conditioning unit. Currently, another approach is to eliminate the air conditioning unit and add a fan coil unit. This involves diverting a portion of the coolant supply to the fan coil unit, which then delivers cool air. However, in most cases, due to the high coolant temperature, it is difficult to achieve dehumidification of the cabin through condensation. If an additional air conditioning indoor unit is used, distributing the refrigerant from one refrigerant system to its evaporator is equivalent to two evaporators in parallel in a vapor compression refrigeration system. Similarly, without designing two evaporation pressures, it is difficult to achieve dehumidification of the cabin. For example, if the load requires a supply coolant temperature of 25°C, diverting a portion of the coolant to the fan coil unit would require the heat exchanger fin surface temperature in the fan coil unit to be approximately 29°C, meaning the cabin air dew point temperature must be above 29°C for dehumidification to be achieved. If an additional indoor air conditioning unit is used, and the evaporation temperature on both the coolant side and the air side is 20°C, then the surface temperature of the evaporator fins of the indoor unit will be approximately 24°C. In other words, the dew point temperature of the cabin air must be higher than 24°C for dehumidification of the cabin air to be achieved.

[0004] In the refrigeration and freezing industry, to achieve both high-temperature and low-temperature storage, when using a single compressor refrigeration system, the common practice is to connect an evaporator pressure regulator to the outlet of the evaporator providing temperature assurance for the high-temperature storage. This regulator is then manually adjusted to increase the evaporator pressure in the high-temperature storage, maintaining a relatively high and constant evaporator pressure, ultimately allowing the evaporators in both the high-temperature and low-temperature storage to reach their respective suitable evaporation temperatures. However, using this type of evaporator pressure regulator makes it difficult to achieve intelligent adjustment between the two temperature zones.

[0005] It is worth exploring how to make a vapor compression refrigeration system more effectively handle two temperature requirements and respond quickly by controlling some valves when the requirements or external environment change, so as to achieve product intelligence and miniaturization. Utility Model Content

[0006] This invention provides a dynamically controllable dual evaporator system to solve the problems of inconvenient adjustment and slow response of evaporators in existing compressor refrigeration systems.

[0007] To achieve the above objectives, the technical solution adopted by this utility model is as follows: A dynamically controllable dual evaporator system includes a throttling element A (1), an evaporator A (2), an electronic control valve A (3), an electronic control valve B (8), a solenoid valve C (4), a throttling element C (5), an evaporator C (6), and a check valve C (7). The outlet of the throttling element A (1) is connected to the inlet of the evaporator A (2), and the outlet of the evaporator A (2) is connected to the inlet of the electronic control valve A (3); the inlet of the electronic control valve B (8) is connected in parallel to the inlet of the throttling element A (1), and the outlet of the electronic control valve B (8) is connected in parallel to the outlet of the electronic control valve A (3); the inlet of the solenoid valve C (4) is connected in parallel to the inlet of the throttling element A (1) and the inlet of the electronic control valve B (8), the outlet of the solenoid valve C (4) is connected to the inlet of the throttling element C (5), the outlet of the throttling element C (5) is connected to the inlet of the evaporator C (6), and the outlet of the evaporator C (6) is connected to the one-way valve C (…). The inlet of 7) and the outlet of check valve C (7) are connected in parallel to the outlet of electronic control valve A (3) and the outlet of electronic control valve B (8); thus forming a refrigerant parallel structure consisting of three branches, wherein the first branch is formed by throttling element A (1), evaporator A (2) and electronic control valve A (3), the second branch is formed by electronic control valve B (8), and the third branch is formed by solenoid valve C (4), throttling element C (5), evaporator C (6) and check valve C (7), with the parallel inlet as the refrigerant input end of the refrigerant parallel structure and the parallel outlet as the refrigerant output end of the refrigerant parallel structure; Evaporator A (2) and evaporator C (6) can operate simultaneously, or one of them can operate alone. When evaporator A (2) operates alone, solenoid valve C (4) is in the closed state. When evaporator C (6) operates alone, electronic control valve A (3) is in the closed state. When evaporator A (2) and evaporator C (6) operate simultaneously, both solenoid valve C (4) and electronic control valve A (3) are in the open state.

[0008] Furthermore, both electronic control valve A (3) and electronic control valve B (8) are proportional regulating valves; the different evaporation pressures required by evaporator A (2) are achieved by proportionally opening electronic control valve A (3); when the refrigerant output end temperature is overheated in the refrigerant parallel structure, the refrigerant output end temperature is controlled by proportionally opening electronic control valve B (8); when electronic control valve A (3) is fully open, the evaporation pressures in evaporator A (2) and evaporator C (6) are in the same state.

[0009] Furthermore, the electronic control valve A (3) adjusts the evaporation pressure in evaporator A (2) to be no less than the evaporation pressure in evaporator C (6).

[0010] Furthermore, both evaporators A (2) and C (6) are air-cooled heat exchangers to achieve cold air output at two different temperatures; or both evaporators A (2) and C (6) are water-cooled heat exchangers to achieve cold liquid output at two different temperatures; or one of evaporators A (2) and C (6) is an air-cooled heat exchanger and the other is a water-cooled heat exchanger to achieve cold air output at one temperature and cold liquid output at one temperature.

[0011] Furthermore, the air-cooled heat exchanger is a tube-fin heat exchanger or a microchannel heat exchanger; the water-cooled heat exchanger is a plate heat exchanger, or a shell-and-tube heat exchanger, or a printed circuit board heat exchanger.

[0012] Furthermore, the throttling element A (1) and the throttling element C (5) are both electronic expansion valves, capillary tubes, or thermostatic expansion valves.

[0013] Compared with the prior art, the advantages of this utility model are: 1. This utility model utilizes the switching and proportional adjustment of two electronic control valves to achieve control of different evaporation pressures and evaporation temperatures on the basis of the original two-way parallel evaporators, while solving the problem of evaporation overheating caused by load or ambient temperature changes.

[0014] 2. This utility model is flexible in application and can be used for cabin air conditioning with two different temperatures, refrigerant equipment with two different temperatures, and composite refrigeration equipment with one liquid cooling and one cold air cooling.

[0015] 3. This utility model can enable two evaporators to work simultaneously or independently.

[0016] 4. This utility model is based on a modular design concept, and its principle is simple, easy to expand and implement. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of an embodiment of this utility model.

[0018] Figure 2 This is a schematic diagram of the structure of a composite refrigeration device with one liquid cooling and one cold air cooling circuit according to an embodiment of the present invention.

[0019] Figure 3 This is a schematic diagram of the structure of a cooling liquid device for two different temperatures according to an embodiment of this utility model.

[0020] Figure 4 This is a schematic diagram of the structure of an air conditioning device for two different temperatures according to an embodiment of this utility model. Detailed Implementation

[0021] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0022] like Figure 1 As shown, this embodiment discloses a dynamically controllable dual evaporator system, including a throttling element A1, an evaporator A2, an electronic control valve A3, a solenoid valve C4, a throttling element C5, an evaporator C6, a one-way valve C7, and an electronic control valve B8. These constitute a refrigerant parallel structure with three branches. The refrigerant input terminal I of the refrigerant parallel structure is used to input high-pressure liquid refrigerant, and the refrigerant output terminal O of the refrigerant parallel structure finally outputs low-pressure gaseous refrigerant.

[0023] The first branch includes a throttling element A1 and an evaporator A2. The outlet of the throttling element A1 is connected to the inlet of the evaporator A2 through a pipeline, and the outlet of the evaporator A2 is connected to the inlet of the electronic control valve A3 through a pipeline.

[0024] The second branch includes electronic control valve B8. The inlet of electronic control valve B8 is connected in parallel to the inlet of throttling element A1 through a pipeline, and the outlet of electronic control valve B8 is connected in parallel to the outlet of electronic control valve A3 through a pipeline.

[0025] The third branch includes solenoid valve C4, throttling element C5, evaporator C6, and check valve C7. The inlet of solenoid valve C4 is connected in parallel to the inlet of throttling element A1 and the inlet of electronic control valve B8 via a pipeline. The outlet of solenoid valve C4 is connected in parallel to the inlet of throttling element C5 via a pipeline. The outlet of throttling element C5 is connected in parallel to the inlet of evaporator C6 via a pipeline. The outlet of evaporator C6 is connected in parallel to the inlet of check valve C7 via a pipeline. The outlet of check valve C7 is connected in parallel to the outlet of electronic control valve A3 and the outlet of electronic control valve B8 via a pipeline.

[0026] In the refrigerant parallel structure, the parallel inlet of throttling element A1, electronic control valve B8, and solenoid valve C4 is used as the refrigerant input terminal I, and the parallel outlet of electronic control valve A3, electronic control valve B8, and check valve C7 is used as the refrigerant output terminal O.

[0027] Electronic control valves A3 and B8 are both proportional control valves. The proportional opening of electronic control valve A3 controls the different evaporation pressures required by evaporator A2. In the parallel refrigerant connection structure, when the refrigerant output temperature is overheated, the proportional opening of electronic control valve B8 controls the refrigerant output temperature. When electronic control valve A3 is fully open, the evaporation pressures in evaporators A2 and C6 are the same. Furthermore, electronic control valve A3 ensures that the evaporation pressure in evaporator A2 is not less than the evaporation pressure in evaporator C6.

[0028] Evaporators A2 and C6 both employ air-cooled heat exchangers to achieve cold air output at two different temperatures; alternatively, evaporators A2 and C6 both employ water-cooled heat exchangers to achieve cold liquid output at two different temperatures; or one of evaporators A2 and C6 employs an air-cooled heat exchanger while the other employs a water-cooled heat exchanger to achieve cold air output at one temperature and cold liquid output at one temperature. The air-cooled heat exchanger is a finned tube heat exchanger or a microchannel heat exchanger; the water-cooled heat exchanger is a plate heat exchanger, a shell-and-tube heat exchanger, a shell-and-tube heat exchanger, or a printed circuit board heat exchanger.

[0029] Throttling element A1 and throttling element C5 are either electronic expansion valves, capillary tubes, or thermostatic expansion valves.

[0030] In this embodiment, evaporators A2 and C6 operate simultaneously, or one of them operates alone. When evaporator A2 operates alone, solenoid valve C4 is in the closed state; when evaporator C6 operates alone, electronic control valve A3 is in the closed state; when evaporators A2 and C6 operate simultaneously, both solenoid valve C4 and electronic control valve A3 are in the open state.

[0031] like Figure 2 The diagram shown is a schematic diagram of the structure of a composite refrigeration equipment with one liquid cooling circuit and one cold air cooling circuit, which is applied in this embodiment. Figure 2 middle Indicates the direction of airflow. Indicates the direction of refrigerant flow. This indicates the direction of coolant flow. In this composite refrigeration equipment structure, the compressor 10 outlet is connected to the condenser 11 inlet via a pipeline. The condenser 11 is equipped with a condenser fan 12, and the condenser 11 outlet is connected to the receiver 13 inlet via a pipeline. The receiver 13 outlet is connected to the dryer filter 14 inlet via a pipeline, and the dryer filter 14 outlet is connected to the sight glass 15 inlet via a pipeline.

[0032] The sight glass 15 outlet is divided into three pipes. The first pipe connects to the inlet of the throttling element A1 in the dual evaporator system of this embodiment. The outlet of throttling element A1 is connected to the inlet of evaporator A2 via a pipe, and the outlet of evaporator A2 is connected to the inlet of electronic control valve A3 via a pipe. The second pipe of the sight glass 15 outlet is connected only to the inlet of electronic control valve B8 in the dual evaporator system of this embodiment. The third pipe of the sight glass 15 outlet connects to the inlet of solenoid valve C4 in the dual evaporator system of this embodiment. The outlet of solenoid valve C4 is connected to the inlet of throttling element C5 via a pipe, the outlet of throttling element C5 is connected to the inlet of evaporator C6 via a pipe, and the outlet of evaporator C6 is connected to the inlet of check valve C7 via a pipe.

[0033] The outlets of electronic control valve A1, electronic control valve B8, and check valve C7 are connected in parallel and then connected to the inlet of gas-liquid separator 15. The outlet of gas-liquid separator 15 returns to the inlet of compressor 10.

[0034] In this composite refrigeration equipment structure, evaporator C6 is equipped with evaporator fan 16, condenser fan 12, and evaporator fan 16 for external heat exchange. Evaporator A2 is a plate heat exchanger. One flow channel of the plate heat exchanger is used to connect throttling element A1 and electronic control valve A3, and the other flow channel of the plate heat exchanger is used for the coolant output from the external liquid cooling system to achieve coolant cooling.

[0035] like Figure 3 The diagram shows the structural schematics of two different temperature-controlled cooling liquid devices using this embodiment. Figure 3 middle Indicates the direction of airflow. Indicates the direction of refrigerant flow. This indicates the direction of coolant flow. The structure of this coolant system is as follows... Figure 2 Based on the composite refrigeration equipment structure shown, the evaporator C6 in the third branch of the dual evaporator system used in this embodiment is replaced with a plate heat exchanger. One flow channel of the evaporator C6 is used to connect the outlet of the throttling element C5 and the inlet of the one-way valve C7, and the other flow channel of the evaporator C6 is used for the coolant output from the external liquid cooling system to pass through so as to cool the coolant. Furthermore, the following is omitted: Figure 2 The evaporator fan 16 in the composite refrigeration equipment structure shown here results in the following: Figure 3 The structure of the cooling liquid equipment is shown.

[0036] like Figure 4 The diagram shows the structural schematics of two different air conditioning devices using this embodiment. Figure 4 middle Indicates the direction of airflow. Indicates the direction of refrigerant flow. This indicates the direction of coolant flow. The structure of this air conditioning unit is such that… Figure 2Based on the composite refrigeration equipment structure shown, the evaporator A2 in the first branch of the dual evaporator system of this embodiment used in the composite refrigeration equipment structure is replaced from a plate heat exchanger to an air-cooled heat exchanger. The air-cooled heat exchanger is used to connect the outlet of the throttling element A1 and the inlet of the electronic control valve A3, and an evaporation fan 17 is configured for the evaporator A2 using the air-cooled heat exchanger.

[0037] The following is a detailed description of a liquid-cooled and cold-air-cooled combined refrigeration unit using the dual-evaporator system of this embodiment: like Figure 2 As shown, in this composite refrigeration equipment structure, evaporators A2 and C6 have the same cooling capacity. Evaporator A2 uses a plate heat exchanger to cool the coolant, while evaporator C6 uses a tube-fin heat exchanger to cool the air. The coolant is a 66% ethylene glycol aqueous solution. The inlet temperature of evaporator A2 is 30℃, and the outlet temperature is 25℃. The design evaporation temperature of evaporator A2 is 20℃, corresponding to an absolute evaporation pressure of 5.72 bar. This pressure is achieved by adjusting the electronic control valve A3; that is, when the opening of electronic control valve A3 decreases, the corresponding evaporation pressure of evaporator A2 increases, and when the opening increases, the corresponding evaporation pressure of evaporator A2 decreases. When fully open, the evaporation pressures in evaporators A2 and C6 remain the same. The design evaporation temperature of evaporator C6 is 7℃, corresponding to an absolute evaporation pressure of 3.75 bar. This pressure is comparable to the compressor suction pressure and is mainly achieved by designing a reasonable heat exchange area for evaporator C6 and adjusting the airflow of the evaporator fan 16. At this point, the evaporator C6 is designed with an evaporation temperature of 7°C, a fin temperature of 11°C, and a dew point temperature of 12°C. This means that the dry bulb temperature inside the cabin is 27°C, and the relative humidity can be reduced to 39.3%, which fully meets the dehumidification requirements of the cabin.

[0038] Once the temperature and humidity inside the cabin reach the required level, the solenoid valve C4 closes and the evaporator C6 stops working. However, the evaporator fan 16 can still work as needed to achieve internal air circulation inside the cabin. At this time, the compressor 10 uses unloading or frequency conversion to achieve matching of the refrigerant working fluid circulation volume.

[0039] When the coolant supply temperature needs to be increased due to load requirements, such as from 25℃ to 40℃; or when the air conditioning ambient temperature rises or during the high-temperature start-up phase, the refrigerant superheat is regulated by electronic control valve B8 to prevent the compressor from activating its protection mechanism.

[0040] When liquid cooling is not required and only cabin temperature regulation is needed, the electronic control valve A3 is closed, and the compressor 10 uses unloading or frequency conversion to match the refrigerant circulation volume.

[0041] When the throttling element C5 is an electronic expansion valve with a shut-off function, the shut-off and opening functions of the solenoid valve C4 are performed by the throttling element C5, and the solenoid valve C4 can be deactivated.

[0042] The following is a detailed description of the two different cold liquid devices using the dual evaporator system of this embodiment: like Figure 3 As shown, in this composite refrigeration equipment structure, both evaporators A2 and C6 use plate heat exchangers to cool the coolant, which is a 66% ethylene glycol aqueous solution. The inlet temperature of evaporator A2 is 30℃, and the outlet temperature is 25℃. The design evaporation temperature of evaporator A2 is 20℃, corresponding to an absolute evaporation pressure of 5.72 bar. This pressure is controlled by adjusting the electronic control valve A3; a smaller opening of valve A3 increases the evaporation pressure of evaporator A2, and a larger opening decreases the evaporation pressure. When fully open, the evaporation pressures in evaporators A2 and C6 remain the same. Evaporator C6 is designed to have an evaporation temperature of 5℃, corresponding to an absolute evaporation pressure of 3.50 bar. This pressure is comparable to the compressor's suction pressure and is primarily achieved through a well-designed heat exchange area for evaporator C6. At this point, the evaporator C6 is designed to evaporate at 5℃, which meets the liquid supply requirements of an inlet temperature of 15℃ and an outlet temperature of 10℃, thus achieving two different temperature liquid supplies. When the evaporator C6 stops working, the solenoid valve C4 can be closed. At this time, the compressor 10 adopts unloading or frequency conversion mode to achieve matching of the refrigerant working fluid circulation volume.

[0043] The following is a detailed description of two air conditioning units operating at different temperatures using the dual evaporator system of this embodiment: like Figure 4As shown, in this composite refrigeration equipment structure, both evaporators A2 and C6 employ tube-fin heat exchangers to cool the air, serving as ambient temperature control for the two compartments respectively. Evaporator A2 is located in the high-temperature compartment. Evaporator A2 has an inlet air temperature of 35°C and an outlet air temperature of 27°C. The designed evaporation temperature of evaporator A2 is 20°C, corresponding to an absolute evaporation pressure of 5.72 bar. This pressure is controlled by adjusting the electronic control valve A3; a smaller opening of valve A3 increases the evaporation pressure of evaporator A2, and a larger opening decreases the evaporation pressure. When fully open, the evaporation pressures in evaporators A2 and C6 remain the same. Evaporator C6 has a designed evaporation temperature of 7°C, corresponding to an absolute evaporation pressure of 3.75 bar. This pressure is comparable to the compressor's suction pressure and is primarily achieved through a well-designed heat exchange area for evaporator C6 and adjustments to the airflow of the evaporator fan 16. At this point, the evaporator C6 is designed with an evaporation temperature of 7℃, a fin temperature of 11℃, and a dew point temperature of 12℃. This means that the dry-bulb temperature inside the cryogenic chamber is 27℃, and the relative humidity can be reduced to 39.3%, which fully meets the dehumidification requirements of the chamber. When the evaporator A2 stops working, the electronic control valve A3 can be closed. At this time, the compressor 10 adopts unloading or frequency conversion mode to achieve matching of the refrigerant circulation volume.

[0044] The preferred embodiments of this utility model have been described in detail above with reference to the accompanying drawings. These embodiments are merely descriptions of preferred embodiments and are not intended to limit the concept and scope of this utility model. The various specific technical features described in the above embodiments can be combined in any suitable manner without contradiction. Such combinations, as long as they do not violate the spirit of this utility model, should also be considered as part of this disclosure. To avoid unnecessary repetition, this utility model will not further describe all possible combinations.

[0045] This utility model is not limited to the specific details of the above embodiments. Within the scope of the technical concept of this utility model and without departing from the design idea of ​​this utility model, all modifications and improvements made by those skilled in the art to the technical solution of this utility model should fall within the protection scope of this utility model. The technical content for which protection is sought in this utility model has been fully recorded in the claims.

Claims

1. A dynamically controllable dual evaporator system, characterized in that, It includes throttling element A (1), evaporator A (2), electronic control valve A (3), electronic control valve B (8), solenoid valve C (4), throttling element C (5), evaporator C (6), and check valve C (7); The outlet of the throttling element A (1) is connected to the inlet of the evaporator A (2), and the outlet of the evaporator A (2) is connected to the inlet of the electronic control valve A (3); the inlet of the electronic control valve B (8) is connected in parallel to the inlet of the throttling element A (1), and the outlet of the electronic control valve B (8) is connected in parallel to the outlet of the electronic control valve A (3); the inlet of the solenoid valve C (4) is connected in parallel to the inlet of the throttling element A (1) and the inlet of the electronic control valve B (8), the outlet of the solenoid valve C (4) is connected to the inlet of the throttling element C (5), the outlet of the throttling element C (5) is connected to the inlet of the evaporator C (6), and the outlet of the evaporator C (6) is connected to the one-way valve C (…). The inlet of 7) and the outlet of check valve C (7) are connected in parallel to the outlet of electronic control valve A (3) and the outlet of electronic control valve B (8); thus forming a refrigerant parallel structure consisting of three branches, wherein the first branch is formed by throttling element A (1), evaporator A (2) and electronic control valve A (3), the second branch is formed by electronic control valve B (8), and the third branch is formed by solenoid valve C (4), throttling element C (5), evaporator C (6) and check valve C (7), with the parallel inlet as the refrigerant input end of the refrigerant parallel structure and the parallel outlet as the refrigerant output end of the refrigerant parallel structure; Evaporator A (2) and evaporator C (6) can operate simultaneously, or one of them can operate alone. When evaporator A (2) operates alone, solenoid valve C (4) is in the closed state. When evaporator C (6) operates alone, electronic control valve A (3) is in the closed state. When evaporator A (2) and evaporator C (6) operate simultaneously, both solenoid valve C (4) and electronic control valve A (3) are in the open state.

2. The dynamically controllable dual evaporator system according to claim 1, characterized in that, The electronic control valves A (3) and B (8) are both proportional control valves. The different evaporation pressures required by the evaporator A (2) are achieved by proportionally opening the electronic control valve A (3). When the refrigerant output temperature in the refrigerant parallel structure is overheated, the temperature of the refrigerant output is controlled by proportionally opening the electronic control valve B (8). When the electronic control valve A (3) is fully open, the evaporation pressures in the evaporator A (2) and the evaporator C (6) are in the same state.

3. The dynamically controllable dual evaporator system according to claim 2, characterized in that, The electronic control valve A (3) adjusts the evaporation pressure in evaporator A (2) to be no less than the evaporation pressure in evaporator C (6).

4. The dynamically controllable dual evaporator system according to claim 1, characterized in that, Evaporator A (2) and evaporator C (6) both use air-cooled heat exchangers to achieve cold air output at two different temperatures; or evaporator A (2) and evaporator C (6) both use water-cooled heat exchangers to achieve cold liquid output at two different temperatures; or one of evaporator A (2) and evaporator C (6) uses an air-cooled heat exchanger and the other uses a water-cooled heat exchanger to achieve cold air output at one temperature and cold liquid output at one temperature.

5. The dynamically controllable dual evaporator system according to claim 4, characterized in that, The air-cooled heat exchanger is a tube-fin heat exchanger or a microchannel heat exchanger; the water-cooled heat exchanger is a plate heat exchanger, a shell-and-tube heat exchanger, a shell-and-tube heat exchanger, or a printed circuit board heat exchanger.

6. The dynamically controllable dual evaporator system according to claim 1, characterized in that, The throttling element A (1) and throttling element C (5) are both electronic expansion valves, capillary tubes, or thermal expansion valves.

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