Heat exchange equipment

Abstract

The utility model discloses heat exchange equipment, and relates to the technical field of heat exchange equipment, the heat exchange equipment comprises an electric control module and a refrigerant circulation system, the refrigerant circulation system comprises a refrigerant circulation loop, and a compressor, a first heat exchanger, an economizer, a first throttle mechanism and a second heat exchanger which are arranged on the refrigerant circulation loop and connected in sequence, the economizer ensures that both the first heat exchanger and the second heat exchanger can obtain proper refrigerant supply, the refrigerant flow and temperature can be finely adjusted, the refrigerant circulation loop comprises a first connecting flow path located between the first heat exchanger and the second heat exchanger, and the first connecting flow path comprises a first heat exchange branch and a first bypass branch which are arranged in parallel. The first heat exchange branch is in heat exchange connection with the electric control module, the first bypass branch and the electric control module are arranged in a spaced mode, part of the refrigerant flows through the first heat exchange branch, part of the refrigerant flows through the first bypass branch, the amount of the refrigerant passing through the first heat exchange branch is reduced, heat taken away by the refrigerant is correspondingly reduced, and the condensation problem is avoided.

Description

Technical Field

[0001] This utility model relates to the field of heat exchange equipment technology, and in particular to a heat exchange equipment. Background Technology

[0002] Variable frequency compressor air source heat pumps are widely used in the market due to their versatility and energy efficiency. However, their control systems generate a significant amount of heat during operation, especially in poorly ventilated or high-temperature environments, where poor heat dissipation can lead to damage to internal components. To address this issue, a method using refrigerant circulation to cool the electronic control module has been proposed. This method utilizes the superior thermal conductivity of liquid refrigerant compared to air to effectively remove the heat generated by the electronic control components, ensuring stable operation of the system.

[0003] While refrigerant circulation systems effectively reduce the temperature of electronic control components, they also present new challenges: in high-humidity environments, condensation may occur on the cooling surfaces, leading to short circuits and failures in the electronic control components. Therefore, when designing such heat dissipation schemes, measures must be taken to prevent condensation to protect the electronic control system. Utility Model Content

[0004] The main purpose of this invention is to propose a heat exchange device that aims to solve the problem that condensation may occur on the cooling surface in high humidity environments, leading to short circuits and failure of electronic control components.

[0005] To achieve the above objectives, the heat exchange device proposed in this utility model includes:

[0006] Electronic control module; and,

[0007] The refrigerant circulation system includes a refrigerant circulation loop and a compressor, a first heat exchanger, an economizer, a first throttling mechanism, and a second heat exchanger that are sequentially connected on the refrigerant circulation loop.

[0008] The refrigerant circulation loop includes a first connecting flow path located between the first heat exchanger and the economizer. The first connecting flow path includes a first heat exchange branch and a first bypass branch arranged in parallel. The first heat exchange branch is heat-exchange connected to the electronic control module, and the first bypass branch is spaced apart from the electronic control module.

[0009] In one embodiment, the economizer includes a first heat exchange flow path and a second heat exchange flow path connected by heat exchange.

[0010] The first heat exchange flow path is connected in the refrigerant circulation loop and is located between the first connecting flow path and the first throttling mechanism;

[0011] One end of the second heat exchange flow path is connected to the pipeline between the first heat exchange flow path and the first connecting flow path, and the other end of the second heat exchange flow path is connected to the return gas port or the make-up gas port of the compressor through a jet branch.

[0012] In one embodiment, the heat exchange device further includes a second throttling mechanism, one end of which is connected to the pipeline between the first heat exchange flow path and the first connecting flow path, and the other end of which is connected to the second heat exchange flow path.

[0013] In one embodiment, the jet branch is heat-exchange connected to the electronic control module.

[0014] In one embodiment, the refrigerant circulation system further includes a distribution device disposed in the first connecting flow path, the distribution device being used to distribute the refrigerant flow of the first heat exchange branch and the first bypass branch.

[0015] In one embodiment, the dispensing device includes a first control valve disposed in the first bypass branch;

[0016] The first control valve includes at least one of a solenoid valve, a switching valve, an electronic expansion valve, a check valve, and a flow control valve.

[0017] In one embodiment, the first control valve includes a first check valve configured to unidirectionally guide the flow path from the second heat exchanger to the first heat exchanger.

[0018] In one embodiment, a second control valve is provided on the first heat exchange branch, and the second control valve includes at least one of a solenoid valve, a switching valve, an electronic expansion valve, a check valve, and a flow control valve.

[0019] In one embodiment, the second control valve includes a second check valve, which is configured to unidirectionally guide the flow path from the first heat exchange branch to the second heat exchanger.

[0020] In one embodiment, the second control valve is located on the side of the electronic control module near the second heat exchanger.

[0021] In one embodiment, the heat exchange device further includes a third throttling mechanism connected in the refrigerant circulation loop and located between the first heat exchanger and the first connecting flow path.

[0022] In one embodiment, the heat exchange device further includes a four-way valve, the four ports of which are respectively connected to the exhaust port of the compressor, the suction port of the compressor, the first heat exchanger, and the second heat exchanger;

[0023] When the heat exchange equipment is running in the first operating mode, the exhaust port of the compressor is sequentially connected to the four-way valve, the first heat exchanger, the third throttling mechanism, the first connecting flow path, the economizer, the first throttling mechanism, the second heat exchanger, the four-way valve, and the intake port of the compressor. The first throttling mechanism throttles the air, the third throttling mechanism is fully open, the first bypass branch is closed, and the first heat exchange branch is open.

[0024] When the heat exchange equipment is running in the second operating mode, the exhaust port of the compressor is sequentially connected to the four-way valve, the second heat exchanger, the first throttling mechanism, the economizer, the first connecting flow path, the third throttling mechanism, the first heat exchanger, the four-way valve and the intake port of the compressor. The first throttling mechanism and the third throttling mechanism throttle the flow, and the first bypass branch and the first heat exchange branch are both open.

[0025] In one embodiment, the pipe diameter of the first heat exchange branch is D0, where 5mm ≤ D0 ≤ 13mm; and / or,

[0026] The diameter of the first bypass branch is D1, where 5mm ≤ D1 ≤ 16mm.

[0027] In one embodiment, the length of the first heat exchange branch is L0, the diameter of the first heat exchange branch is D0, the length of the first bypass branch is L1, the diameter of the first bypass branch is D1, and L1 / L0 = μ(D1 / D0). 5 , where 0.01≤μ≤2.3.

[0028] In one embodiment, the heat exchange device further includes a second heat exchange branch connected in parallel with the first heat exchange branch, a second control valve is provided on the second heat exchange branch, and the second heat exchange branch is heat-exchange connected to the electronic control module.

[0029] In one embodiment, the second control valve includes a second check valve configured to unidirectionally guide the flow path from the first heat exchanger to the second heat exchanger.

[0030] In one embodiment, the second control valve is located on the side of the electronic control module closer to the second heat exchanger.

[0031] In one embodiment, the pipe diameter of the first heat exchange branch is D0, and the pipe diameter of the second heat exchange branch is D2, where D2 = k * D0, 0.7 ≤ k ≤ 1.3, and 5 mm ≤ D2 ≤ 13 mm.

[0032] In one embodiment, the electronic control module includes a circuit board, a heating element, and a heat sink. The heating element is disposed on the circuit board, and the heating element and the heat sink are thermally connected. The first heat exchange branch passes through the heat sink; and / or,

[0033] The jet path is at least partially inserted into the radiator.

[0034] In the technical solution of this utility model, the heat exchange equipment includes a compressor, a first heat exchanger, an economizer, a first throttling mechanism, and a second heat exchanger, which are sequentially connected on the refrigerant circulation loop. The exhaust port of the economizer is connected to the air inlet of the compressor through a jet branch to increase the enthalpy of the compressor by jet injection, ensuring that both the first and second heat exchangers receive appropriate refrigerant supply and enabling fine adjustment of refrigerant flow and temperature. The first connecting flow path includes a first heat exchange branch and a first bypass branch arranged in parallel. When the refrigerant in the refrigerant circulation loop flows to the first connecting flow path, part of the refrigerant flows through the first heat exchange branch and part flows through the first bypass branch. Because the first heat exchange branch is heat-exchange connected to the electronic control module, and the first bypass branch is spaced apart from the electronic control module, the amount of refrigerant passing through the first heat exchange branch is reduced, and the heat carried away by the refrigerant is reduced accordingly. While ensuring the heat dissipation effect, the temperature of the electronic control module will not drop rapidly and will be maintained at a relatively high level, thereby avoiding condensation problems caused by excessively low temperatures. Attached Figure Description

[0035] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0036] Figure 1 This is a schematic diagram of the structure of an embodiment of a heat exchange device in the related technology;

[0037] Figure 2 A schematic diagram of the structure of an embodiment of the heat exchange device provided by this utility model;

[0038] Figure 3 A schematic diagram of another embodiment of the heat exchange device provided by this utility model;

[0039] Figure 4 A schematic diagram of another embodiment of the heat exchange device provided by this utility model;

[0040] Figure 5A schematic diagram of another embodiment of the heat exchange device provided by this utility model;

[0041] Figure 6 A schematic diagram of another embodiment of the heat exchange device provided by this utility model;

[0042] Figure 7 A schematic diagram of another embodiment of the heat exchange device provided by this utility model.

[0043] Explanation of icon numbers:

[0044] 100' Heat exchange equipment; 1' Electrical control module; 10' Refrigerant circulation loop; 7' Economizer;

[0045] 100. Heat exchange equipment; 1. Electrical control module; 10. Refrigerant circulation loop; 2. Compressor; 3. First heat exchanger; 4. Second heat exchanger; 101. First heat exchange branch; 102. First bypass branch; 103. Second heat exchange branch; 104. First heat exchange flow path; 105. Second heat exchange flow path; 106. Jet branch; 5. Distribution device; 51. First electric valve; 52. First check valve; 6. Second control valve; 61. Second electric valve; 62. Second check valve; 7. Economizer; 8. First throttling mechanism; 9. Second throttling mechanism; 11. Third throttling mechanism; 12. Four-way valve; 13. Third control valve; 131. Third check valve.

[0046] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0047] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0048] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0049] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0050] In high-humidity environments, condensation may form on the cooling surfaces of the electronic control module of an air-source heat pump, potentially causing short circuits and malfunctions in the electronic components. Therefore, when designing such heat dissipation solutions, it is essential to consider how to prevent condensation to protect the electronic control system.

[0051] This utility model proposes a heat exchange device 100, which aims to solve the problem that water droplets may condense on the cooling surface in a high humidity environment, causing short circuits and failures of the electronic control components.

[0052] Please see Figures 2 to 5 In one embodiment of this utility model, the heat exchange device 100 includes an electronic control module 1 and a refrigerant circulation system. The refrigerant circulation system includes a refrigerant circulation loop 10 and a compressor 2, a first heat exchanger 3, an economizer 7, a first throttling mechanism 8, and a second heat exchanger 4, which are sequentially connected on the refrigerant circulation loop 10. The refrigerant circulation loop 10 includes a first connecting flow path located between the first heat exchanger 3 and the second heat exchanger 4. The first connecting flow path includes a first heat exchange branch 101 and a first bypass branch 102 arranged in parallel. The first heat exchange branch 101 is heat-exchange connected to the electronic control module 1, and the first bypass branch 102 is spaced apart from the electronic control module 1.

[0053] It should be noted that in cooling mode, the ambient temperature is relatively high, the heat dissipation requirement of the electronic control module 1 is large, and the possibility of condensation on the electronic control module 1 is low; in heating mode, the ambient temperature is relatively low, the heat dissipation requirement of the electronic control module 1 is small, and the possibility of condensation on the electronic control module 1 is high. Therefore, in the following description, the reduction of the risk of condensation will mainly focus on the case of heating mode.

[0054] In a heat pump system, the functions of the first heat exchanger 3 and the second heat exchanger 4 can be determined according to the system's operating mode (cooling or heating) and the direction of refrigerant flow. The first heat exchanger 3 and the second heat exchanger 4 can function as either condensers or evaporators under different operating conditions. The following explains the changes in the heat exchanger roles under these two modes:

[0055] In cooling mode, the heat pump extracts heat from the indoor space and releases it into the outdoor environment.

[0056] The first heat exchanger 3 (usually located outdoors) acts as a condenser: the refrigerant, which has become a high-temperature, high-pressure gas, releases heat here, condenses back into a liquid state, and releases the heat to the outdoor air.

[0057] The second heat exchanger 4 (usually located indoors) acts as an evaporator: the refrigerant changes from liquid to gas here, absorbing heat from the indoor air, thereby cooling the indoor environment.

[0058] In heating mode, the heat pump operates in reverse to extract heat from the outdoor environment and transfer it indoors to heat the space.

[0059] The second heat exchanger 4 (usually located outdoors) acts as an evaporator: the refrigerant absorbs heat from the outside environment here. Even if the outside temperature is low, it can still absorb heat from the outside air through the reverse Carnot cycle, and then be pressurized and heated by the compressor 2.

[0060] The second heat exchanger 4 (usually located indoors) acts as a condenser: at this time, the refrigerant is pressurized by the compressor 2 and enters this heat exchanger. Here, the refrigerant changes from a gaseous state to a liquid state, releasing heat to the indoor air and heating the indoor environment.

[0061] In this embodiment, please refer to Figure 2 The following description uses the following modes: the refrigerant flows from the compressor 2 into the first heat exchanger 3, then into the second heat exchanger 4, and finally back to the compressor 2 in cooling mode; and the refrigerant flows from the compressor 2 into the second heat exchanger 4, then into the first heat exchanger 3, and finally back to the compressor 2 in heating mode.

[0062] It should also be noted that, please refer to Figure 1In the heat exchange device 100 of the related technology, all the refrigerant in the refrigerant circulation loop 10 flows through the heat exchange connection with the electronic control module 1. In this embodiment, the first connection flow path includes the first heat exchange branch 101 and the first bypass branch 102 arranged in parallel. This means that when the refrigerant flows through the refrigerant circulation loop 10, only a portion flows through the first heat exchange branch 101, and the other portion flows through the first bypass branch 102 and then merges with the refrigerant flowing out of the first heat exchange branch 101. In other words, the amount of refrigerant passing through the first heat exchange branch 101 is less than the amount of refrigerant in the related technology.

[0063] It should be noted that the prototype of the economizer 512 is a heat exchanger. Part of the refrigerant flowing out of the first heat exchanger 3 is throttled through the subcooling throttling valve and further cooled by thermal expansion to lower the temperature of the other part, making it subcooled. The subcooled liquid refrigerant then enters the second heat exchanger 4 for refrigeration. The other part of the uncooled gaseous refrigerant re-enters the compressor 1 through the jet branch for further compression and enters the cycle to improve system capacity and efficiency.

[0064] The economizer 7 is connected to the gas supply port or gas return port of the compressor 2. That is, in the heating mode, part of the liquid refrigerant in the refrigerant circulation loop flows through the first connecting flow path and part of the refrigerant flows through the economizer 7. The amount of refrigerant in the first connecting flow path is reduced, so the amount of refrigerant in the first heat exchange branch 101 will be reduced accordingly, thereby further reducing the heat carried away.

[0065] According to the basic formula for heat transfer, Q1 = CGmΔT, Q is the heat transferred per unit time, C is the specific heat capacity of the refrigerant (i.e., the heat required to raise the temperature of a unit mass of substance by one degree); Gm is the mass flow rate of the refrigerant (the amount of refrigerant passing through the first heat exchange branch 101 per unit time); and ΔT is the temperature difference between the refrigerant and the electronic control module 1.

[0066] Reducing the refrigerant flow rate through the first heat exchange branch 101 effectively reduces the value of G. Since Q is proportional to G, reducing G directly leads to a decrease in the heat Q transferred to the refrigerant. As less heat is carried away by the refrigerant, the cooling rate of the electronic control module 1 slows down accordingly. Because the refrigerant carries away less heat, the cooling rate of the electronic control module 1 decreases, allowing its surface temperature to be maintained at a higher level.

[0067] It is understandable that the amount of refrigerant required for the first heat exchange branch 101 is determined based on the heat exchange demand corresponding to the current condensation point. The pipe diameter of the first heat exchange branch 101 is then determined based on the amount of refrigerant. Alternatively, the pipe diameter of the first bypass branch 102 is determined based on the amount of refrigerant to be allocated to it.

[0068] It should also be noted that "the first heat exchange branch 101 is heat exchanged with the electronic control module 1" means that the first heat exchange branch 101 and the electronic control module 1 can be in direct contact heat exchange or indirect contact heat exchange, ensuring that heat can be effectively transferred from the electronic control module 1 to the relatively low-temperature refrigerant, and then dissipated through the refrigerant circulation system.

[0069] "The first bypass branch 102 is spaced apart from the electronic control module 1" means that the first bypass branch 102 and the electronic control module 1 are not connected for heat exchange; no heat exchange occurs between them, and the electronic control module 1 cannot carry away its heat through the low-temperature refrigerant in the first bypass branch 102. Specifically, insulation can be achieved by maintaining a considerable distance between them or by using an insulation structure.

[0070] In the technical solution of this utility model, the heat exchange device 100 includes a compressor 2, a first heat exchanger 3, an economizer 7, a first throttling mechanism 8, and a second heat exchanger 4, which are sequentially connected on the refrigerant circulation loop 10. The exhaust port of the economizer 7 is connected to the air supply port of the compressor 2 through a jet branch to increase the enthalpy of the air jet from the compressor 2, ensuring that both the first heat exchanger 3 and the second heat exchanger 4 receive appropriate refrigerant supply and avoiding local overheating or overcooling. The first connecting flow path includes a first heat exchange branch 101 and a first bypass branch 102 arranged in parallel, which are located in the refrigerant circulation loop 10. When the refrigerant in the refrigerant circulation loop 10 flows to the first connecting flow path, part of the refrigerant flows through the first heat exchange branch 101 and part of the refrigerant flows through the first bypass branch 102. Since the first heat exchange branch 101 is heat exchanged with the electronic control module 1, and the first bypass branch 102 is spaced apart from the electronic control module 1, the amount of refrigerant passing through the first heat exchange branch 101 is reduced, and the heat carried away by the refrigerant is reduced accordingly. While ensuring the heat dissipation effect, the temperature of the electronic control module 1 will not drop rapidly and will be maintained at a relatively high level, thereby avoiding condensation problems caused by excessively low temperature.

[0071] Specifically, in this embodiment, the economizer 7 includes a first heat exchange flow path 104 and a second heat exchange flow path 105 connected by heat exchange; the first heat exchange flow path 104 is connected in the refrigerant circulation loop and is located between the first connecting flow path and the first throttling mechanism 8; one end of the second heat exchange flow path 105 is connected to the pipeline between the first heat exchange flow path 104 and the first connecting flow path, and the other end of the second heat exchange flow path 105 is connected to the return gas port or the make-up gas port of the compressor 2 through the jet branch 106.

[0072] Understandably, the second heat exchange flow path 105 is connected to the return gas port of the compressor 2 for heat recovery, pre-cooling the refrigerant in the main cycle, and increasing the subcooling. When the second heat exchange flow path 105 is connected to the gas supply port of the compressor 2, it is used to supply gas to the compressor 2 in the intermediate stage, increasing the refrigerant flow rate.

[0073] In this embodiment, the heat exchange device 100 further includes a second throttling mechanism 9, one end of which is connected to the pipeline between the first heat exchange flow path 104 and the first connecting flow path, and the other end of which is connected to the second heat exchange flow path 105.

[0074] The second throttling mechanism 9 is used to convert high-pressure liquid refrigerant into low-pressure, low-temperature refrigerant. The second throttling mechanism 9 is installed on the pipeline between the second heat exchange flow path 105 and the first connecting flow path. During refrigeration, the refrigerant flows through the second throttling mechanism 9, causing its temperature to drop. This results in the refrigerant temperature in the second heat exchange flow path 105 being lower than that in the first heat exchange flow path 104, thereby facilitating heat exchange between the first heat exchange flow path 104 and the second heat exchange flow path 105. The lower temperature of the refrigerant flowing through the second heat exchange flow path 105 to the compressor 2 achieves the purpose of increasing subcooling or increasing refrigerant flow rate.

[0075] Further, please refer to Figure 6 and Figure 7 In another embodiment, the jet branch 106 is heat-exchange connected to the electronic control module 1.

[0076] It is understandable that the refrigerant flowing through the first connecting flow path is a subcooled liquid with a high specific heat capacity, which can absorb more heat, while the refrigerant in the jet branch 106 is a gaseous refrigerant with a low specific heat capacity and a relatively weak heat absorption capacity, which can carry away less heat from the electronic control module 1.

[0077] The gaseous refrigerant that is not subcooled by the economizer 7 returns to the return or replenishment port of the compressor 2 via the jet branch 106. The overall heat absorption capacity of the first connecting flow path and the jet branch 106, which are connected to the electronic control module 1 for heat exchange, is smaller than that when the liquid refrigerant flows entirely through the first connecting flow path without the economizer. Correspondingly, the heat carried away by the refrigerant is reduced. In this way, while ensuring the heat dissipation effect, the temperature of the electronic control module 1 is not reduced excessively and is kept at a relatively high level, thereby avoiding condensation problems caused by excessively low temperature.

[0078] Further, please refer to Figure 2In this embodiment, the refrigerant circulation system further includes a distribution device 5, which is disposed in the first connecting flow path and is used to distribute the refrigerant flow of the first heat exchange branch 101 and the first bypass branch 102.

[0079] It is understood that the distribution device 5 can dynamically adjust the amount of refrigerant flowing into the first heat exchange branch 101 and the first bypass branch 102 according to the system's operating status or environmental conditions. This is to optimize heat dissipation efficiency and prevent the surface temperature of the electronic control module 1 from becoming too low.

[0080] The distribution device 5 can be installed on the first heat exchange branch 101. Directly mounted on the first heat exchange branch 101, the distribution device 5 is used to regulate the refrigerant flow rate entering this branch. The heat exchange intensity between the refrigerant and the electronic control module 1 is controlled by limiting or increasing the flow rate. Its structure is simple, and it is easy to achieve independent control of the flow rate in the first heat exchange branch 101.

[0081] The distribution device 5 can be installed on the first bypass branch 102 to adjust the refrigerant flow rate bypassing the first heat exchange branch 101. This adjustment is achieved by indirectly influencing the amount of refrigerant flowing through the first heat exchange branch 101. This allows for greater flexibility in adjusting the bypass flow rate without affecting the main heat exchange path.

[0082] The distribution device 5 can also be set at the intersection of the first heat exchange branch 101 and the first bypass branch 102, i.e., a three-way valve or other type of distributor. In this way, the proportion of refrigerant flowing into the two branches can be directly controlled to provide distribution flexibility, accurately distribute the refrigerant flow as needed, accurately control the cooling rate of the electronic control module 1, maintain its surface temperature within a range that will not cause condensation, and ensure the best heat dissipation effect and anti-condensation performance.

[0083] For details, please continue reading Figure 2 and Figure 3 In this embodiment, the distribution device 5 includes a first control valve disposed in the first bypass branch 102; the first control valve includes at least one of a solenoid valve, a switching valve, an electronic expansion valve, a check valve, and a flow control valve. Thus, the amount of refrigerant in the first heat exchange branch 101 is adjusted indirectly without affecting the main path, avoiding any impact on the normal operation of the entire heat exchange system due to malfunctions caused by the first control valve.

[0084] The flow control valve can be a first electric valve 51. An electric valve is a device that uses a motor as a power source to control the opening, closing, or adjustment of the valve opening degree via electrical signals. When it receives an electrical signal from the control system, the motor inside the electric valve starts, driving the valve core to move, thereby changing the flow area of ​​the fluid (refrigerant in this example) to achieve flow control. Thus, the electric valve can automatically adjust its opening degree according to preset parameters or real-time feedback to precisely control the refrigerant flow through the first heat exchange branch 101 and the first bypass branch 102. This optimizes heat dissipation and prevents condensation caused by excessively low surface temperature of the electronic control module 1. The electric valve is connected to the system's central controller, receiving data input from devices such as temperature and humidity sensors to achieve intelligent adjustment based on environmental conditions (temperature and humidity). By connecting to a network or control system, the status of the electric valve can be monitored and adjusted remotely, increasing the system's convenience and response speed.

[0085] Specifically, in order to save costs, in some other embodiments, please refer to Figure 3 The first control valve includes a first check valve 52, which is configured to unidirectionally guide the flow path from the second heat exchanger 4 to the first heat exchanger 3.

[0086] A check valve (also known as a non-return valve) is a valve that allows fluid to flow in only one direction, preventing reverse flow. When fluid flows in from the designated inlet, the valve core inside the check valve automatically opens, allowing the fluid to pass through; when an attempt is made to flow in the opposite direction from the outlet, the valve core closes, preventing backflow.

[0087] In the refrigerant circulation system, the first one-way valve 52 ensures that the refrigerant can only flow from the second heat exchanger 4 to the first heat exchanger 3, and cannot flow in the opposite direction. That is, in the corresponding operating mode (heating mode) when the refrigerant flows from the second heat exchanger 4 to the first heat exchanger 3, the refrigerant circulation loop 10 can achieve refrigerant diversion.

[0088] Further, please refer to Figure 6 and Figure 7 In another embodiment, a second control valve 6 is provided on the first heat exchange branch 101. The second control valve 6 includes at least one of a solenoid valve, a switching valve, an electronic expansion valve, a check valve, and a flow control valve. Optionally, the second control valve 6 may be configured as a second electric valve 61.

[0089] The second control valve 6 can adjust the flow rate on the first heat exchange branch 101, so that the adjustment range of the amount of refrigerant exchanging heat with the electronic control module 1 can be adjusted within a larger threshold range.

[0090] In addition, when the first control valve malfunctions, the second control valve 6 can assist in regulating the amount of refrigerant that exchanges heat with the electronic control module 1.

[0091] Furthermore, to save costs, please continue to refer to... Figure 7 In some embodiments, the second control valve 6 includes a second check valve 62, which is configured to unidirectionally guide the flow path from the first heat exchanger 3 to the second heat exchanger 4.

[0092] In the refrigerant circulation system, the second one-way valve 62 ensures that the refrigerant can only flow from the first heat exchanger 3 to the second heat exchanger 4, and cannot flow in the opposite direction. That is, in the corresponding operating mode (cooling mode) when the refrigerant flows from the first heat exchanger 3 to the second heat exchanger 4, the refrigerant circulation loop 10 can achieve refrigerant diversion.

[0093] In cooling mode, the refrigerant flows from the first heat exchanger 3 to the second heat exchanger 4. At this time, the first one-way valve 51 is in the closed state, while the second one-way valve 62 is in the open state, and all the refrigerant is connected to the electronic control module 1 for heat exchange.

[0094] In heating mode, refrigerant flows from the second heat exchanger 4 to the first heat exchanger 3. At this time, the first one-way valve 51 is in the open state, while the second one-way valve 62 is in the closed state. Part of the refrigerant flows through the first heat exchange branch 101, and part of the refrigerant flows through the first bypass branch 102. Therefore, only the refrigerant in the first heat exchange branch 101 is connected to the electronic control module 1 for heat exchange, thus avoiding the generation of condensation.

[0095] Furthermore, in this embodiment, the third control valve 13 is located on the side of the electronic control module 1 near the second heat exchanger 4.

[0096] It is understood that the third control valve 13 cuts off the refrigerant in the second heat exchange branch in the cooling mode. In the heating mode, when the liquid refrigerant flows from the second heat exchanger 4 to the first heat exchanger 3, the third control valve 13 can block the low-temperature liquid refrigerant on the side of the electronic control module 1 near the second heat exchanger 4, thereby avoiding heat exchange with the electronic control module 1.

[0097] Furthermore, the heat exchange device 100 also includes a third throttling mechanism 11, which is connected in the refrigerant circulation loop 10 and located between the first heat exchanger 3 and the first connecting flow path.

[0098] The third throttling mechanism 11 is disposed between the first heat exchanger 3 and the first connecting flow path. The third throttling mechanism 11 is set to fully open in cooling mode and to throttle in heating mode. Thus, in heating mode, the refrigerant temperature is appropriately reduced before entering the first heat exchanger 3, resulting in a lower return gas temperature when entering the compressor 2. The compressor 2 consumes less energy when processing gas, thereby improving the compressor's thermal efficiency and overall energy efficiency.

[0099] Furthermore, in this embodiment, the heat exchange device 100 also includes a four-way valve 12, the four ports of which are respectively connected to the exhaust port of the compressor 2, the intake port of the compressor 2, the first heat exchanger 3, and the second heat exchanger 4.

[0100] It should be noted that the four-way valve 12 is used to switch the refrigerant flow direction. The four-way valve 12 can change the refrigerant flow path, allowing the refrigerant to flow in reverse between the two heat exchangers, thereby switching the operating mode of each heat exchanger. When the four-way valve 12 switches, the heat exchanger that was originally an evaporator becomes a condenser, and the original condenser becomes an evaporator. Thus, the heat exchange device 100 can achieve two operating modes: a first operating mode (cooling mode) and a second operating mode (heating mode).

[0101] When the heat exchanger 100 is running in the first operating mode, the exhaust port of the compressor 2 is sequentially connected to the four-way valve 12, the first heat exchanger 3, the third throttling mechanism 11, the first connecting flow path, the economizer 7, the first throttling mechanism 8, the second heat exchanger 4, the four-way valve 12, and the intake port of the compressor 2. The first throttling mechanism 8 throttles the air, the third throttling mechanism 11 is fully open, the first bypass branch 102 is closed, and the first heat exchange branch 101 is open.

[0102] The first operating mode is set to cooling mode. After the high-pressure liquid refrigerant flows out from the first heat exchanger 3, it first passes through the third throttling mechanism 11. In cooling mode, the third throttling mechanism 11 is fully open, and the main circuit refrigerant enters the economizer at high pressure at the condenser outlet without throttling. The high-pressure liquid refrigerant evaporates and absorbs heat in the economizer 7 through the second heat exchange path 105 (throttled by the second throttling mechanism 9), significantly increasing the subcooling of the main circuit refrigerant in the first heat exchange path 104.

[0103] It should be noted that the second throttling mechanism 9 and the first throttling mechanism 8 throttle the gas supply flow of the second heat exchange path 105 by throttling the second throttling mechanism 9, thereby avoiding overload of the compressor 2 and ensuring that the evaporation process in the economizer 7 fully absorbs heat and maximizes the subcooling effect.

[0104] The first throttling mechanism 8 throttles the subcooled main circuit refrigerant to the evaporation pressure, allowing it to enter the second heat exchanger 4 to absorb heat. Due to the increased subcooling, the effective cooling capacity of the second heat exchanger 4 is improved.

[0105] High-pressure liquid refrigerant enters directly into the economizer 7, and the evaporation process in the second heat exchange path 105 can cool the main circuit more efficiently. The gas supply is precisely adjusted through the second throttling mechanism 9 to avoid overloading the compressor 2 and improve the cycle efficiency.

[0106] The third throttling mechanism 11 is fully open to ensure that the high-pressure liquid refrigerant enters the economizer. The second heat exchange flow path 105 forms a low-pressure evaporation branch after being throttled by the second throttling mechanism 9, which forms a significant temperature difference with the main circuit (the first heat exchange flow path 104), thereby enhancing the heat exchange effect and increasing the subcooling.

[0107] When the heat exchanger 100 is running in the second operating mode, the exhaust port of the compressor 2 is sequentially connected to the four-way valve 12, the second heat exchanger 4, the first throttling mechanism 8, the economizer 7, the first connecting flow path, the third throttling mechanism 11, the first heat exchanger 3, the four-way valve 12 and the suction port of the compressor. Both the first throttling mechanism 8 and the third throttling mechanism 11 throttle the flow, and both the first bypass branch 102 and the first heat exchange branch 101 are open.

[0108] It should be noted that the second operating mode is set to heating mode. In heating mode, in order to adapt to the pressure gradient of reverse flow, the third throttling mechanism 11 and the first throttling mechanism 8 are throttled, and the second throttling mechanism 9 is fully open.

[0109] The reduced heat exchange temperature difference (pressure difference between the second heat exchange path 105 and the first heat exchange path 104) within the economizer 7 results in a limited increase in subcooling. The second throttling mechanism 9 is fully open, and the third throttling mechanism 11 throttles the refrigerant in the main circuit before it enters the economizer 7, reducing its pressure. The heat exchange direction of the economizer 7 is adjusted to ensure that the subcooling still optimizes heating performance.

[0110] Specifically, in this embodiment, the pipe diameter of the first heat exchange branch 101 is D0, 5mm≤D0≤13mm; and / or, the pipe diameter of the first bypass branch 102 is D1, 5mm≤D1≤16mm.

[0111] Understandably, according to Q=λA*(△t / δ)=Q1, Q is the heat transferred per unit time (watts, W); λ is the thermal conductivity of the material (W / m·K), representing the material's ability to conduct heat; A is the heat transfer area (square meters, m2), i.e., the surface area of ​​the refrigerant pipe in contact with the surrounding medium; Δt is the temperature difference (Kelvin, K), i.e., the temperature difference between the refrigerant and the electronic control module 1; δ is the thickness of the heat transfer path (meters, m), which in this scenario can be understood as the thickness of the refrigerant pipe wall; Q1 represents the actual heat to be transferred. It can be seen that the pipe diameter directly affects the refrigerant's flow rate and velocity, thus affecting heat dissipation efficiency. A smaller pipe diameter leads to higher fluid resistance and pressure loss, while a larger pipe diameter may result in excessively low flow velocity, affecting the heat exchange effect.

[0112] The pipe diameters of the first heat exchange branch 101 and the first bypass branch 102 are set within the above-mentioned range to ensure that the pipe size of the refrigerant circulation system can meet the effective heat exchange requirements without introducing additional problems due to improper size, so as to maintain the efficient operation, stability and reliability of the system.

[0113] Preferably, the pipe diameter of the first heat exchange branch 101 is D0, 6mm≤D0≤10mm; and / or, the pipe diameter of the first bypass branch 102 is D1, 6mm≤D1≤13mm.

[0114] The pipe diameter of the first heat exchange branch 101 can be set to 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm... and the pipe diameter of the first bypass branch 102 can be set to 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm, 10mm, 10.5mm, 11mm, 11.5mm, 12mm, 12.5mm... In this way, both the first heat exchange branch 101 and the first bypass branch 102 are in the optimal state in terms of manufacturability and performance.

[0115] Specifically, in this embodiment, the length of the first heat exchange branch 101 is L0, the diameter of the first heat exchange branch 101 is D0, the length of the first bypass branch 102 is L1, the diameter of the first bypass branch 102 is D1, L1 / L0=μ(D1 / D0)5, where 0.01≤μ≤2.3.

[0116] L0 and pipe diameter D0 directly affect the heat exchange area. A longer pipe length and an appropriate pipe diameter can increase the contact area between the refrigerant and the electronic control module 1, thereby improving the heat exchange efficiency.

[0117] Smaller pipe diameters result in higher fluid resistance and pressure loss, while larger pipe diameters may lead to excessively low flow rates. By adjusting L1 and D1 using the formula above, sufficient flow rate can be ensured while minimizing fluid resistance and reducing pumping energy consumption.

[0118] The existence of the first bypass branch 102 allows the system to adjust the amount of refrigerant entering the first heat exchange branch 101 as needed. By precisely setting L1 and D1, sufficient refrigerant can be ensured to participate in the actual heat exchange, while preventing excessive refrigerant from bypassing the heat exchange process.

[0119] By setting the relationship between L1 / L0 and D1 / D0, it is ensured that the refrigerant flow rates in the first heat exchange branch 101 and the first bypass branch 102 can be reasonably matched under different operating conditions. This avoids the refrigerant flow rate in one branch being too fast or too slow, which would affect the heat dissipation effect.

[0120] Further, please refer to Figure 4 and Figure 5 In another embodiment, the first connection flow path further includes a second heat exchange branch 103 arranged in parallel with the first heat exchange branch 101, the second heat exchange branch 103 is provided with a third control valve 13, and the second heat exchange branch 103 is heat exchanged with the electronic control module 1.

[0121] The third control valve 13 can adjust the flow rate on the second heat exchange branch 103, so that the amount of refrigerant that exchanges heat with the electronic control module 1 can be adjusted within a wider threshold range.

[0122] Furthermore, when the first control valve malfunctions, the third control valve 13 can assist in adjusting the amount of refrigerant that exchanges heat with the electronic control module 1.

[0123] Specifically, to save costs, please continue reading Figure 4 and Figure 5 In some embodiments, the third control valve 13 includes a third check valve 131, which is configured to unidirectionally guide the flow path from the first heat exchanger 3 to the second heat exchanger 4.

[0124] In the refrigerant circulation system, the third one-way valve 131 ensures that the refrigerant can only flow from the first heat exchanger 3 to the second heat exchanger 4, and cannot flow in the opposite direction. That is, in the corresponding operating mode (cooling mode) when the refrigerant flows from the first heat exchanger 3 to the second heat exchanger 4, the refrigerant circulation loop 10 can achieve refrigerant diversion.

[0125] In cooling mode, the refrigerant flows from the first heat exchanger 3 to the second heat exchanger 4. At this time, the first one-way valve 52 is in the closed state, while the third one-way valve 131 is in the open state, and all refrigerant is connected to the electronic control module 1 for heat exchange.

[0126] In heating mode, refrigerant flows from the second heat exchanger 4 to the first heat exchanger 3. At this time, the first one-way valve 52 is in the open state, while the third one-way valve 131 is in the closed state. Part of the refrigerant flows through the first heat exchange branch 101, and part of the refrigerant flows through the first bypass branch 102. Therefore, only the refrigerant in the first heat exchange branch 101 is connected to the electronic control module 1 for heat exchange, thus avoiding the generation of condensation.

[0127] Furthermore, in this embodiment, the electronic control module 1 includes a substrate and electronic components disposed on the substrate; the second heat exchange branch 103 is at least partially embedded in the substrate.

[0128] By embedding the second heat exchange branch 103 into the substrate, the refrigerant can directly contact the interior of the substrate that generates heat, thereby greatly improving the heat exchange efficiency, reducing the accumulation of heat in the substrate, and saving the space required for external additional heat dissipation devices. This makes the entire electronic control module 1 more compact, which is conducive to miniaturization and lightweight design.

[0129] Furthermore, in this embodiment, the third control valve 13 is located on the side of the electronic control module 1 near the second heat exchanger 4.

[0130] It is understood that the third control valve 13 cuts off the refrigerant on the second heat exchange branch 103 in the cooling mode. In the heating mode, when the liquid refrigerant flows from the second heat exchanger 4 to the first heat exchanger 3, the third control valve 13 can block the low-temperature liquid refrigerant on the side of the electronic control module 1 near the second heat exchanger 4, thereby avoiding heat exchange with the electronic control module 1.

[0131] Furthermore, in this embodiment, the pipe diameter of the first heat exchange branch 101 is D0, and the pipe diameter of the second heat exchange branch 103 is D2, where D2 = k * D0, 0.7 ≤ k ≤ 1.3, and 5 mm ≤ D2 ≤ 13 mm.

[0132] By setting D2 = k * D0, the pipe diameters of the two heat exchange branches are ensured to vary within a reasonable range, allowing for a smooth transition in refrigerant flow between the two branches. This helps maintain stable system operation and avoids flow mismatch problems caused by excessive differences in pipe diameter.

[0133] Under different operating conditions, the electronic control module 1 and other components requiring cooling may have different heat dissipation requirements. By adjusting the proportional coefficient k, it is possible to ensure effective heat dissipation of one branch without affecting the working efficiency of another branch. For example, in some cases, appropriately reducing the pipe diameter of the second heat exchange branch 103 can concentrate more refrigerant flow to the first heat exchange branch 101, thereby improving its heat dissipation effect.

[0134] The specific value of k can be 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, etc.

[0135] Understandably, smaller pipe diameters increase fluid resistance and pressure loss, while larger diameters may result in excessively low flow rates. By keeping D2 and D0 within a relatively close range, the fluid resistance of the entire system can be effectively controlled, pumping energy consumption reduced, and sufficient flow rate ensured for effective heat exchange.

[0136] Specifically, the heat exchange device 100 includes an air heat source pump. An air heat source pump is a device that utilizes heat from outdoor air to provide heating, cooling, and hot water for a building. It operates on the principle of a reverse Carnot cycle, that is, through an electrically driven compressor 2 system, it absorbs low-grade heat energy from the environment and converts it into high-grade heat energy for indoor heating or cooling. The air heat source pump can be used in a combined heating and cooling water system.

[0137] Specifically, the electronic control module 1 includes a circuit board, a heating element, and a heat sink. The heating element is disposed on the circuit board, and the heating element and the heat sink are heat-transfer connected. The first heat exchange branch 101 passes through the heat sink.

[0138] The first heat exchange branch 101 is inserted into the heat sink, and the heat sink can fully contact the first heat exchange branch 101 directly. The heat sink can fully transfer the heat of the heat-generating device to the first heat exchange branch 101, thereby greatly improving the heat exchange efficiency, reducing the accumulation of heat in the circuit board and the heat-generating device, and saving the space required for external additional heat dissipation devices. This makes the entire electronic control module 1 more compact, which is conducive to miniaturization and lightweight design.

[0139] Of course, the jet branch 106 can also be embedded in the radiator to improve heat exchange efficiency.

[0140] It should be noted that the heat sink is made of a material with high thermal conductivity, such as aluminum, copper, or stainless steel.

[0141] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A heat exchange apparatus, characterized by, The heat exchange device comprises: an electric control module; a refrigerant circulation system comprising a refrigerant circulation loop, and a compressor, a first heat exchanger, an economizer, a first throttling mechanism and a second heat exchanger connected in sequence on the refrigerant circulation loop; wherein the refrigerant circulation loop comprises a first connection flow path between the first heat exchanger and the economizer, the first connection flow path comprising a first heat exchange branch and a first bypass branch arranged in parallel, the first heat exchange branch being in heat exchange connection with the electric control module, and the first bypass branch being arranged apart from the electric control module. The economizer comprises a first heat exchange flow path and a second heat exchange flow path in heat exchange connection; 2. The heat exchanging apparatus according to claim 1, wherein the first heat exchange flow path is connected in the refrigerant circulation loop and located between the first connection flow path and the first throttling mechanism; one end of the second heat exchange flow path is connected to a pipeline between the first heat exchange flow path and the first connection flow path, and the other end of the second heat exchange flow path is connected to a back gas port or a gas supplement port of the compressor through a jet branch. The heat exchange device further comprises a second throttling mechanism, one end of the second throttling mechanism is connected to the pipeline between the first heat exchange flow path and the first connection flow path, and the other end of the second throttling mechanism is connected to the second heat exchange flow path.

3. The heat exchange apparatus according to claim 2, wherein The jet branch is in heat exchange connection with the electric control module.

4. The heat exchange apparatus according to claim 2, wherein The refrigerant circulation system further comprises a distribution device arranged in the first connection flow path, the distribution device being used for distributing refrigerant flow of the first heat exchange branch and the first bypass branch.

5. The heat exchange apparatus according to claim 1, wherein The distribution device comprises a first control valve arranged in the first bypass branch; 6. The heat exchange apparatus according to claim 5, wherein The first control valve comprises at least one of an electromagnetic valve, an on-off valve, an electronic expansion valve, a check valve and a flow control valve. The first control valve comprises a first check valve arranged to unidirectionally guide a flow path from the second heat exchanger to the first heat exchanger.

7. The heat exchange apparatus according to claim 6, wherein A second control valve is arranged on the first heat exchange branch, the second control valve comprising at least one of an electromagnetic valve, an on-off valve, an electronic expansion valve, a check valve and a flow control valve.

8. The heat exchange apparatus according to claim 1, wherein The second control valve comprises a second check valve arranged to unidirectionally guide a flow path from the first heat exchange branch to the second heat exchanger.

9. The heat exchange apparatus according to claim 8, wherein The second control valve is arranged on a side of the electric control module close to the second heat exchanger.

10. The heat exchange apparatus according to claim 8, wherein The heat exchange device further comprises a third throttling mechanism connected in the refrigerant circulation loop and located between the first heat exchanger and the first connection flow path.

11. The heat exchanging apparatus according to any one of claims 1 to 10, wherein The heat exchange device further comprises a four-way valve, four ports of the four-way valve being respectively connected to an exhaust port of the compressor, a suction port of the compressor, the first heat exchanger and the second heat exchanger; 12. The heat exchange apparatus of claim 11, wherein ​ When the heat exchange device operates in the first operation mode, the exhaust port of the compressor is sequentially communicated with the four-way valve, the first heat exchanger, the third throttling mechanism, the first connecting flow path, the economizer, the first throttling mechanism, the second heat exchanger, the four-way valve and the suction port of the compressor, the first throttling mechanism throttles, the third throttling mechanism fully opens, the first bypass branch is cut off, and the first heat exchange branch is conducted. When the heat exchange device operates in the second operation mode, the exhaust port of the compressor is sequentially communicated with the four-way valve, the second heat exchanger, the first throttling mechanism, the economizer, the first connecting flow path, the third throttling mechanism, the first heat exchanger, the four-way valve and the suction port of the compressor, the first throttling mechanism and the third throttling mechanism throttle, and the first bypass branch and the first heat exchange branch are both conducted.

13. The heat exchange apparatus of claim 1, wherein The pipe diameter of the first heat exchange branch is D0, and 5mm≤D0≤13mm; and / or, The pipe diameter of the first bypass branch is D1, and 5mm≤D1≤16mm.

14. The heat exchanging device according to any one of claims 1 to 10, 13, wherein The tube length of the first heat exchange branch is L0, the tube diameter of the first heat exchange branch is D0, the tube length of the first bypass branch is L1, the tube diameter of the first bypass branch is D1, and L1 / L0 = μ 5 wherein 0.01 ≤ μ ≤ 2.

3.

15. The heat exchanging device according to any of claims 1 to 10, 13, wherein The heat exchange device further comprises a second heat exchange branch which is arranged in parallel with the first heat exchange branch, a third control valve is arranged on the second heat exchange branch, and the second heat exchange branch is in heat exchange connection with the electric control module.

16. The heat exchange apparatus of claim 15, wherein The third control valve comprises a third one-way valve which is arranged to unidirectionally conduct the flow path from the first heat exchanger to the second heat exchanger.

17. The heat exchange apparatus of claim 15, wherein The third control valve is arranged on the side of the electric control module close to the second heat exchanger.

18. The heat exchange apparatus of claim 15, wherein, The pipe diameter of the first heat exchange branch is D0, the pipe diameter of the second heat exchange branch is D2, and D2=k*D0, wherein 0.7≤k≤1.3, and 5mm≤D2≤13mm.

19. The heat exchange apparatus of claim 2, wherein The electric control module comprises a circuit board, a heating device and a heat sink, the heating device is arranged on the circuit board, the heating device and the heat sink are in heat transfer connection, and the first heat exchange branch is arranged in the heat sink; and / or, The jet branch is at least partially arranged in the heat sink.

Images