Double-temperature-zone water-air heat exchanger core for heat pump system

Abstract

The utility model relates to the technical field of automobile heat pump system, specifically disclose a double temperature zone water air heat exchanger core for heat pump system. The core includes the first collecting pipe of intercommunication two water inlet pipes, the second collecting pipe, third collecting pipe and fourth collecting pipe connected in proper order through micro -tubing, wherein the second and third collecting pipe interval set overflow hole, fourth collecting pipe connects water outlet pipe. The core inside flows through coolant, and carries out cold and warm two -way heat exchange with air through micro -tubing. The water inlet pipe is connected with three -way valve, and the independent temperature control of double temperature zone is realized through the adjustment two -way flow proportion. Its joint layout provides two kinds of implementation ways: scheme one supports the flexible positioning of water inlet pipe joint between the partition and end cover, and scheme two adopts integrated joint integrated import and export pipeline. The scheme eliminates the risk of R290 refrigerant leakage through indirect heat exchange of coolant, reduces the flow resistance through the design of overflow hole, and the double-inlet flow distribution mechanism breaks through the temperature zone control limitation of traditional single-flow path evaporator.

Description

Technical Field

[0001] This utility model belongs to the field of automotive air conditioning heat pump systems, and relates to a dual-temperature zone water-air heat exchanger core for heat pump systems. Background Technology

[0002] In existing automotive heat pump systems, traditional evaporator cores typically employ a design with direct refrigerant heat exchange. In such devices, the refrigerant flows into the core through a single inlet, undergoes heat exchange, and then flows out through an outlet. The inlet and outlet often feature asymmetrical pipe layouts. When this structure is applied to systems using the flammable and explosive R290 refrigerant, it inherently presents a safety risk due to refrigerant leakage. Furthermore, the traditional single-flow-path design cannot meet the functional requirements of independent temperature control in both vehicle zones, and the difference in pipe size can easily create significant flow resistance as the coolant flows through the core, reducing system efficiency. Although various evaporator optimization schemes have been proposed in relevant literature, none have resolved the safety hazards of direct R290 refrigerant heat exchange and the compatibility issues with dual-zone temperature control.

[0003] To address these shortcomings, the industry has attempted to develop indirect heat exchange systems to isolate the R290 refrigerant from the passenger compartment. However, existing indirect heat exchangers mostly employ a single-inlet, single-outlet flow path design, which cannot meet the needs of heat pump systems for independent temperature control in multiple zones. Furthermore, the coolant flow path layout in traditional core structures does not adequately consider flow resistance optimization, which can easily lead to increased energy consumption in complex piping systems. Utility Model Content

[0004] In view of this, the purpose of this utility model is to provide a heat exchange device that combines safety, dual-temperature zone control capability and low flow resistance characteristics to meet the application requirements of R290 heat pump systems.

[0005] To achieve the above objectives, this utility model provides the following technical solution: A dual-temperature zone water-air heat exchanger core for a heat pump system includes: two inlet pipes and one outlet pipe; a first manifold connected to the inlet pipes; a second manifold, a third manifold, and a fourth manifold; multiple micro-channels connecting the first manifold to the second, third, and fourth manifolds; and the fourth manifold connected to the outlet pipe.

[0006] Optionally, a flow passage is provided between the second manifold and the third manifold.

[0007] Optionally, the water inlet pipe is configured to connect to a three-way valve to independently adjust the flow rate and achieve dual-temperature zone control.

[0008] Optionally, coolant flows inside the core and exchanges heat with air through microtubes.

[0009] Optionally, the connector of the water inlet pipe is located at the end of the manifold.

[0010] Optionally, the core includes a first end cap and a second end cap arranged opposite to each other, and a partition is provided between the first end cap and the second end cap (K3) to divide the core into two independent heat exchange zones.

[0011] Optionally, the connector of the water inlet pipe is located in the area between the partition and the first end cap, and / or in the area between the partition and the second end cap.

[0012] Optionally, the connector of the water outlet pipe is located on the fourth manifold.

[0013] Optionally, the inlet pipe and outlet pipe are connected to the first manifold and the fourth manifold via an integrated connector.

[0014] Optionally, the flow passage extends through the second and third manifolds, allowing the coolant to flow laterally between the manifolds.

[0015] The beneficial effects of this utility model are as follows: This solution achieves multiple technological breakthroughs in heat pump systems through innovative core structure design: Intrinsic safety improvement Instead of R290 refrigerant, the core uses coolant for heat exchange with the air via a closed-loop system of manifold → microtube → manifold. This design physically isolates the flammable refrigerant from the passenger compartment, completely eliminating the risk of R290 leaks and explosions. Compared to traditional direct-exchange evaporators, safety is significantly improved.

[0016] Dual-zone precise control The dual inlet pipes are connected to a three-way valve, which, together with the independent heat exchange zones separated by the partition, enables dynamic flow distribution: the coolant is diverted through the inlet pipe to the first manifold, and then enters the corresponding zone through the micro-channel 5; the flow holes between the manifolds promote flow balance between the two zones and avoid local overheating / overcooling; by adjusting the three-way valve to change the flow ratio, the temperature of the left and right temperature zones can be independently controlled (such as cooling in the driver's area / heating in the passenger area).

[0017] Flow resistance optimization and energy efficiency gain Traditional evaporators generate high flow resistance due to differences in inlet and outlet dimensions. This solution optimizes the flow path through a three-stage manifold series structure: the coolant flows laterally through the manifold → through the flow hole → manifold to reduce pressure loss; the micro-tubes are evenly distributed to improve the utilization rate of the heat exchange area and reduce eddy current energy consumption.

[0018] Strong structural compatibility Two flexible implementation schemes are provided: Split-type connector (Option 1): The inlet pipe connector can be placed at any position between the partition and the end cap, adapting to complex pipeline layouts. Integrated connector 7 (Option 2): Integrates three pipelines, reducing welding points and leakage risks, and reducing space occupation.

[0019] System functional scalability The core supports bidirectional coolant flow, allowing for seamless switching between cooling and heating modes by changing the direction of the water pump. Combined with dual-temperature zone control, it can create a thermal management scenario where cooling and heating zones operate simultaneously, meeting the comfort needs of electric vehicles in all seasons.

[0020] Other advantages, objectives, and features of this invention will be set forth in part in the description which follows, and in part will be apparent to those skilled in the art from the following examination and study, or may be learned from practice of this invention. The objectives and other advantages of this invention can be realized and obtained through the following description. Attached Figure Description

[0021] To make the objectives, technical solutions, and advantages of this utility model clearer, the preferred embodiments of this utility model will be described in detail below with reference to the accompanying drawings, wherein: Figure 1 This is a schematic diagram of the structure of Embodiment 1; Figure 2 This is a schematic diagram of the structure of Example 2; Figure 3 This is a schematic diagram of the integrated connector in Embodiment 2; Figure 4 This is a schematic diagram of a dual-temperature zone control principle that adjusts the inlet water flow rate via a three-way valve.

[0022] Reference numerals in the attached drawings: First manifold (1), First manifold (2), Second manifold (3), Third manifold (4), Micro-channel (5), Inlet pipe connector (6, 7), Connector (8), First end cap (K2), Second end cap (K3), Partition (K1). Detailed Implementation

[0023] The following specific examples illustrate the implementation of this utility model. Those skilled in the art can easily understand other advantages and effects of this utility model from the content disclosed in this specification. This utility model can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of this utility model. It should be noted that the illustrations provided in the following embodiments are only schematic representations of the basic concept of this utility model. Unless otherwise specified, the following embodiments and features can be combined with each other.

[0024] The accompanying drawings are for illustrative purposes only and are schematic diagrams, not actual pictures. They should not be construed as limiting the present invention. To better illustrate the embodiments of the present invention, some parts in the drawings may be omitted, enlarged, or reduced, and do not represent the actual product dimensions. It is understandable to those skilled in the art that some well-known structures and their descriptions may be omitted in the drawings.

[0025] In the accompanying drawings of this utility model, the same or similar reference numerals correspond to the same or similar components. In the description of this utility model, it should be understood that if terms such as "upper," "lower," "left," "right," "front," and "rear" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting this utility model. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0026] Please see Figures 1-4 This solution provides a dual-temperature zone water-air heat exchanger core for R290 heat pump systems. For example... Figure 2 As shown, the core includes two inlet pipes A and B and one outlet pipe C. Inlet pipes A and B are connected to a first manifold 1, which is connected to a second manifold 2 and a third manifold 3 via multiple micro-channels 5. A flow passage (not labeled in the figure) is provided between the second and third manifolds 2 and 3, allowing the coolant to flow laterally between the two manifolds. The third manifold 3 is connected to a fourth manifold 4 via micro-channels 5, and the fourth manifold 4 is connected to the outlet pipe C.

[0027] The water inlet pipes A and B are configured with external three-way valves, enabling dual-temperature zone control by independently adjusting the flow rate of the two inlet pipes. Coolant, rather than refrigerant, flows inside the core. The coolant exchanges heat with the air as it flows through microtube 5, allowing for either cooling or heating modes to be implemented according to system requirements.

[0028] Example 1: The core has a first end cap K2 and a second end cap K3 at both ends, with a partition K1 separating the two to divide them into two independent heat exchange zones. The connector 6 of the inlet pipe A is located in the area between the partition K1 and the first end cap K2, and the connector 7 of the inlet pipe B is located in the area between the partition K1 and the second end cap K3. The connector 8 of the outlet pipe C is fixed to the third manifold 4. This design allows for flexible adjustment of the connector positions according to piping layout requirements.

[0029] Example 2: Inlet pipes A and B and outlet pipe C are connected to the first manifold 1 and the fourth manifold 4 via an integrated inlet pipe connector 7. The connector 6 of inlet pipe A must be located between the partition K1 and the first end cap K2. The integrated inlet pipe connector 7 integrates the two inlet pipes and the outlet pipe, significantly saving installation space.

[0030] Workflow: The coolant is diverted to inlet pipes A and B via a three-way valve, flows into the first manifold 1, and is then evenly distributed to the micro-channel pipe 5, subsequently entering the second manifold 2 and the third manifold 3. The coolant flow is redistributed through the flow-through orifice between the two manifolds, then flows through the micro-channel pipe 5 into the fourth manifold 4, and finally exits from the outlet pipe C. By adjusting the three-way valve to change the flow ratio between the two inlet pipes, the temperature of the heat exchange zones on both sides can be independently controlled.

[0031] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of this utility model and are not intended to limit it. Although this utility model has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solution of this utility model without departing from the spirit and scope of this technical solution, and all such modifications or substitutions should be covered within the scope of the claims of this utility model.

Claims

1. A dual-temperature zone water-air heat exchanger core for a heat pump system, characterized in that, include: Two inlet pipes (A, B) and one outlet pipe (C); The first manifold (1) is connected to the water inlet pipes (A, B); Second manifold (2), third manifold (3) and fourth manifold (4); Multiple micro-channels (5) connect the first manifold (1) with the second manifold (2), the third manifold (3), and the fourth manifold (4); The fourth manifold (4) is connected to the outlet pipe (C).

2. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 1, characterized in that, A flow passage is provided between the second manifold (2) and the third manifold (3).

3. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 1, characterized in that, The water inlet pipes (A and B) are configured to connect to three-way valves to independently adjust the flow rate and achieve dual-temperature zone control.

4. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 1, characterized in that, Coolant flows inside the core and exchanges heat with air through a microtube (5).

5. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 1, characterized in that: The inlet pipe joints (6, 7) of the inlet pipes (A, B) are located at the end of the first manifold (1).

6. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 5, characterized in that, The core includes a first end cap (K2) and a second end cap (K3) arranged opposite to each other. A partition (K1) is provided between the first end cap (K2) and the second end cap (K3) to divide the core into two independent heat exchange zones.

7. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 6, characterized in that, The inlet pipe joints (6, 7) of the inlet pipes (A, B) are located at: The area between the partition (K1) and the first end cap (K2), and / or The area between the partition (K1) and the second end cap (K3).

8. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 6, characterized in that, The connector (8) of the outlet pipe (C) is located on the fourth manifold (4).

9. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 1, characterized in that: The inlet pipe (A, B) and outlet pipe (C) are connected to the first manifold (1) and the fourth manifold (4) through the inlet pipe connector (7).

10. The dual-temperature zone water-air heat exchanger core for a heat pump system according to claim 2, characterized in that: The flow passage connects the second manifold (2) and the third manifold (3), allowing the coolant to flow laterally between the manifolds.

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