Refrigerant runner block and thermal management refrigerant module

Abstract

Provided are a refrigerant flow path block (100, 200, 200A) and a thermal management refrigerant module (1, 2, 2A) that require a small configuration space and have high suitability. The refrigerant flow path block is integrally formed, has a plurality of refrigerant flow paths (110-190, 210-290) formed therein, and has first outer surfaces (101, 201) to sixth outer surfaces (106, 206), and the refrigerant flow paths (110-190, 210-290) are formed on at least two of the first outer surfaces to the sixth outer surfaces (106, 206), and the refrigerant flow paths (110-190, 210-290) are formed in the refrigerant flow paths (110-190, 210-290). Ports (P1-P3, P1 '-P3', P4 ', P5', P7 ') through which a refrigerant directly enters and exits the refrigerant flow path in the refrigerant flow path block from the heat exchanger are respectively provided, and valve mounting ports (81, 82) through which valves (V1, V2) are inserted into the refrigerant flow path are provided on at least one of the first to sixth outer surfaces except the at least two outer surfaces.

Description

Technical Field

[0001] This utility model relates to a refrigerant flow channel block and a thermal management refrigerant module having the refrigerant flow channel block. Background Technology

[0002] In a thermal management refrigerant module, the refrigerant flow path needs to be switched to achieve different operating modes. As described in Patent Document 1, the existing thermal management refrigerant module has a plate-shaped refrigerant flow channel plate, a heat exchanger, and valves, with the heat exchanger and valves respectively arranged on both sides of the flow channel plate.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: China Utility Model Authorization Announcement No. CN 220314650U.

[0006] Technical problem to be solved by the utility model

[0007] However, in such thermal management refrigerant modules with refrigerant flow path switching capabilities, the flow channel plate is relatively large in its extension direction because the valves and heat exchangers are positioned on the same surface as the flow channel plate. This results in a longer refrigerant flow path within the flow channel plate, leading to increased heat loss and pressure loss, reduced heat exchange efficiency, increased refrigerant charge, and increased overall vehicle power consumption. Furthermore, the longer refrigerant flow path makes it easier for oil to accumulate, further reducing heat exchange efficiency. Moreover, the large space required for the refrigerant flow channel plate and the fixed positions of the heat exchangers and valves make it difficult to adapt to different vehicle models. Utility Model Content

[0008] Therefore, this utility model was made in view of the above-mentioned technical problems, and one of its objectives is to provide a refrigerant flow channel block that requires little configuration space and has high adaptability. Another objective of this utility model is to provide a thermal management refrigerant module having the above-mentioned refrigerant flow channel block.

[0009] Technical means for solving technical problems

[0010] To achieve the above objectives, one aspect of this utility model is a refrigerant flow channel block, which is integrally formed and has multiple refrigerant flow channels for refrigerant flow inside. The refrigerant flow channel block has: a first outer surface and a second outer surface opposite to each other in the length direction; a third outer surface and a fourth outer surface opposite to each other in the height direction; and a fifth outer surface and a sixth outer surface opposite to each other in the width direction. Ports are respectively provided on at least two of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface, allowing refrigerant to directly enter and exit the refrigerant flow channels in the refrigerant flow channel block from the heat exchanger. A valve mounting port for inserting valves into the refrigerant flow channels is provided on at least one of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface, excluding the at least two outer surfaces.

[0011] According to this structure, since the heat exchanger and valves are not located on the same side of the refrigerant channel block, the length of a single side of the refrigerant channel block can be reduced. Compared with existing plate-shaped channel structure, it saves required configuration space, is easier to adapt to different vehicle models, and reduces manufacturing costs. Furthermore, by shortening the length of the refrigerant channel inside the refrigerant channel block, heat and pressure losses are reduced, thus lowering the risk of oil accumulation and improving heat exchange efficiency. In addition, since valves can be arranged on multiple outer surfaces of the refrigerant channel block not used for heat exchangers, the design freedom of valves can be increased, further improving the adaptability of the refrigerant channel block. Moreover, since the refrigerant channel block is integrally formed and the refrigerant channel is formed internally, compared to a split structure formed by multiple components, sealing performance is improved, preventing refrigerant leakage. Furthermore, since the heat exchanger is directly installed on the refrigerant channel block, additional connecting pipes can be omitted, reducing heat and pressure losses, lowering manufacturing costs, and further preventing refrigerant leakage.

[0012] In one possible embodiment, in the above-mentioned refrigerant flow channel block, the plurality of refrigerant flow channels include at least refrigerant flow channels extending along the length direction, the width direction and the height direction respectively.

[0013] According to this structure, by utilizing a three-dimensional refrigerant channel extending in three intersecting directions, the length of the refrigerant channel can be shortened, the overall volume of the refrigerant channel block can be reduced, and the pressure loss and heat loss within the refrigerant channel block can be decreased.

[0014] In one possible embodiment, in the aforementioned refrigerant flow channel block, the at least two outer surfaces on which the port is provided include a first outer surface and a second outer surface.

[0015] According to this structure, since heat exchangers can be arranged on opposite outer surfaces of the refrigerant flow channel block, the refrigerant flow channel can be simplified and shortened, thereby reducing heat loss and pressure loss.

[0016] In one possible embodiment, in the aforementioned refrigerant flow channel block, the at least two outer surfaces on which the ports are provided further include the fifth outer surface.

[0017] According to this structure, the heat exchanger can be arranged on opposite and / or adjacent outer surfaces of the refrigerant channel block, thus shortening the length of the refrigerant channel and reducing heat and pressure losses. Furthermore, this structure increases the flexibility of heat exchanger configuration, thereby improving the adaptability of the refrigerant channel block.

[0018] In one possible embodiment, in the refrigerant flow channel block described above, a sensor mounting port for inserting a sensor into the refrigerant flow channel is provided on at least one of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface.

[0019] Based on this structure, a sensor can be installed on any outer surface of the refrigerant flow channel block. This allows for sensor configuration according to available space or actual needs, facilitating easy detection of refrigerant temperature and pressure while increasing the flexibility of sensor placement, thereby improving the adaptability of the refrigerant flow channel block.

[0020] In one possible embodiment, in the above-mentioned refrigerant channel block, the ratio of the maximum dimensions of the refrigerant channel block in the length direction, the width direction, and the height direction is 1:0.8 to 1.2:0.8:1.2.

[0021] Based on this structure, by setting the refrigerant flow channel block as a column with its maximum dimensions in the length, width, and height directions being approximately equal, the required configuration space for the refrigerant flow channel block can be minimized, thereby increasing the overall design freedom of the thermal management refrigerant module. Furthermore, this columnar structure allows for the installation of valves on various outer surfaces of the refrigerant flow channel block, thus enabling flexible design of valve installation positions according to the configuration requirements of different vehicle models, increasing the configuration freedom of the valves, and consequently improving the adaptability of the refrigerant flow channel block.

[0022] Another aspect of this utility model is a thermal management refrigerant module, comprising the refrigerant flow channel block, a first heat exchanger and a second heat exchanger serving as the heat exchanger, and the valve.

[0023] According to the thermal management refrigerant module with the aforementioned refrigerant channel block, since the heat exchanger and valves are not located on the same side of the refrigerant channel block, the length of a single side of the refrigerant channel block can be reduced. Compared with existing thermal management refrigerant modules, it saves required configuration space, is easier to adapt to different vehicle models, and reduces manufacturing costs. Furthermore, since the length of the refrigerant channel inside the refrigerant channel block can be shortened, heat loss and pressure loss are reduced, thus reducing the risk of oil accumulation and improving heat exchange efficiency. In addition, since valves can be arranged on multiple outer surfaces of the refrigerant channel block that are not used for heat exchangers, the configuration freedom of the valves can be increased, thereby increasing the design freedom of the thermal management refrigerant module and further improving its adaptability. Moreover, since the refrigerant channel block is integrally formed and the refrigerant channel is formed internally, compared with a split structure formed by multiple parts, the sealing performance can be improved, preventing refrigerant leakage. Moreover, since the heat exchanger is directly installed in the refrigerant flow channel block, additional connecting pipes can be omitted, reducing costs, further reducing heat and pressure losses, reducing the configuration space of the thermal management refrigerant module, and further preventing refrigerant leakage.

[0024] In one possible embodiment, in the above-described thermal management refrigerant module, the refrigerant inlet port and / or refrigerant outlet port of the first heat exchanger and the second heat exchanger, respectively, for allowing refrigerant to enter and exit the refrigerant flow channel block are directly connected to the port of the refrigerant flow channel block. The first heat exchanger and the second heat exchanger are directly mounted on the first outer surface and the second outer surface, respectively, and the valve is inserted into the third outer surface.

[0025] According to this structure, since the heat exchanger is not located on the same side of the refrigerant channel block as the valves, the length of a single side of the refrigerant channel block can be reduced. This saves the overall configuration space required for the thermal management refrigerant module and makes it easier to adapt to different vehicle models. Furthermore, since the heat exchanger can be arranged on opposite outer surfaces of the refrigerant channel block, the refrigerant channel can be simplified and shortened, reducing heat and pressure losses in the thermal management refrigerant module.

[0026] In one possible embodiment, the thermal management refrigerant module described above further includes a third heat exchanger, which is directly mounted on the fifth outer surface. The refrigerant inlet port and refrigerant outlet port of the third heat exchanger are directly connected to the ports of the refrigerant flow channel block, respectively.

[0027] According to this structure, the thermal management refrigerant module can be configured as a T-shaped structure with the first and second heat exchangers arranged opposite each other and the third heat exchanger arranged adjacent to the first and second heat exchangers. Therefore, the thermal management refrigerant module can be made more compact and the required configuration space can be reduced while further improving the heat exchange performance.

[0028] In one possible embodiment, the thermal management refrigerant module further includes a sensor for detecting the temperature and / or pressure of the refrigerant flowing in the refrigerant channel. The sensor is inserted into at least one of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface of the refrigerant channel block.

[0029] Based on this structure, a sensor can be installed on any outer surface of the refrigerant flow channel block. This allows for sensor configuration based on available space or actual needs, facilitating easy detection of refrigerant temperature and pressure while increasing the flexibility of sensor placement, thereby improving the adaptability of the thermal management refrigerant module.

[0030] In one possible embodiment, in the above-described thermal management refrigerant module, the thermal management refrigerant module further includes an evaporator for evaporating the refrigerant. The plurality of refrigerant channels of the refrigerant channel block include a first channel, a second channel, and a third channel extending along the length direction; a fourth channel and a fifth channel extending along the height direction; a sixth channel and a seventh channel extending along the width direction; and an eighth channel. The first channel is connected to the refrigerant outlet port of the first heat exchanger, the second channel is connected to the refrigerant inlet port of the second heat exchanger, and the third channel... The fourth flow channel is connected to the refrigerant outlet port of the second heat exchanger. The fifth flow channel connects the first flow channel and the second flow channel. The sixth flow channel is connected to the refrigerant inlet port of the evaporator. The seventh flow channel is connected to the refrigerant outlet port of the evaporator. The refrigerant flowing out of the seventh flow channel and the refrigerant flowing out of the third flow channel merge in the fifth flow channel. The eighth flow channel connects the sixth flow channel and the first flow channel. The refrigerant flowing out of the first flow channel branches into the fourth flow channel and the eighth flow channel.

[0031] Based on this structure, by utilizing multiple channels extending in different directions within the refrigerant flow channel block, the thermal management refrigerant module can form a structure that connects the second heat exchanger and the evaporator in parallel. Furthermore, by utilizing the fourth and fifth channels extending along the height direction, the refrigerant can flow vertically, further reducing the risk of oil accumulation.

[0032] In one possible embodiment, in the above-described thermal management refrigerant module, when viewed from the width direction, an air groove extending along the height direction is provided at the location between the fifth flow channel, the sixth flow channel, and the eighth flow channel of the refrigerant flow channel block.

[0033] According to this structure, the high-temperature and low-temperature regions of the refrigerant flow channel block are insulated by the air slot, which can effectively avoid heat loss caused by heat conduction in the refrigerant flow channel block.

[0034] In one possible embodiment, in the above-described thermal management refrigerant module, the valve includes a first expansion valve and a second expansion valve, the first expansion valve being inserted into the sixth flow channel from the third outer surface, and the second expansion valve being inserted into the second flow channel from the third outer surface.

[0035] Based on this structure, valves are installed for different heat exchangers using the refrigerant flow channel block, thereby enabling the thermal management refrigerant module to easily switch between different operating modes.

[0036] In one possible embodiment, the thermal management refrigerant module described above can switch between a standalone cooling mode, a cooling-cooling mode, and a heating mode. The standalone cooling mode is a mode that cools the air inside the vehicle cabin, the cooling-cooling mode is a mode that cools the air inside the vehicle cabin and the heating device, and the heating mode is a mode that heats the air inside the vehicle cabin. In the standalone cooling mode, the first expansion valve is set to a throttling state, and the second expansion valve is closed. In the cooling-cooling mode, both the first and second expansion valves are set to a throttling state. In the heating mode, the first expansion valve is closed, and the second expansion valve is set to a throttling state.

[0037] Based on this structure, it is possible to easily switch between individual cooling mode, cooling-cooling mode and heating mode using two expansion valves.

[0038] In one possible embodiment, in the above-described thermal management refrigerant module, the third heat exchanger is an intermediate heat exchanger that allows a relatively high-temperature refrigerant to exchange heat with a relatively low-temperature refrigerant. The thermal management refrigerant module also includes an evaporator for evaporating the refrigerant. The plurality of refrigerant channels include a first channel, a second channel, and a third channel extending along the length direction; a fourth channel and a fifth channel extending along the height direction; a sixth channel, a seventh channel, and an eighth channel extending along the width direction. The first channel is connected to the refrigerant outlet port of the first heat exchanger, the second channel is connected to the refrigerant inlet port of the second heat exchanger, and the third channel is connected to the refrigerant outlet port of the second heat exchanger. The fourth flow channel connects the first flow channel and the second flow channel; the fifth flow channel connects the third flow channel and the seventh flow channel; the sixth flow channel is connected to the high-temperature refrigerant inlet port of the third heat exchanger; the refrigerant flowing out of the first flow channel branches into the fourth and sixth flow channels; the seventh flow channel is connected to the low-temperature refrigerant outlet port of the third heat exchanger; the refrigerant flowing out of the seventh flow channel merges with the refrigerant flowing out of the third flow channel in the fifth flow channel; one end of the eighth flow channel is connected to the refrigerant inlet port of the evaporator, and the other end is connected to the high-temperature refrigerant outlet port of the third heat exchanger; the refrigerant outlet port of the evaporator is connected to the low-temperature refrigerant inlet port of the third heat exchanger.

[0039] According to this structure, by utilizing multiple channels extending in different directions in the refrigerant flow channel block, the thermal management refrigerant module can improve the heat exchange efficiency through the third heat exchanger while forming a structure that connects the second heat exchanger and the evaporator in parallel.

[0040] In one possible embodiment, in the above-described thermal management refrigerant module, the valve includes a first expansion valve and a second expansion valve, the first expansion valve being inserted into the eighth flow channel from the third outer surface, and the second expansion valve being inserted into the second flow channel from the third outer surface.

[0041] Based on this structure, valves can be set separately for different heat exchangers, thereby enabling the thermal management refrigerant module to easily switch between different operating modes.

[0042] In one possible embodiment, in the above-described thermal management refrigerant module, the valve includes a first expansion valve and a second expansion valve, the first expansion valve being inserted into the eighth flow channel from the fourth outer surface, and the second expansion valve being inserted into the second flow channel from the sixth outer surface.

[0043] Based on this structure, valves can be individually installed for different heat exchangers, allowing the thermal management refrigerant module to easily switch between different operating modes. Furthermore, the valve placement can be designed according to actual needs, increasing the flexibility of valve configuration and further enhancing the adaptability of the thermal management refrigerant module to different vehicle models.

[0044] In one possible embodiment, in the above-described thermal management refrigerant module, when viewed along the length direction, the rectangular projected area of ​​the refrigerant channel block formed by the maximum dimensions in the width direction and the height direction is greater than the rectangular projected areas of the first heat exchanger and the second heat exchanger, but does not exceed 2.3 times the rectangular projected areas of the first heat exchanger and the second heat exchanger.

[0045] According to this structure, by reducing the dimensions of the refrigerant flow channel block in the height and width directions, the required configuration space for the thermal management refrigerant module in the height and width directions can be reduced.

[0046] In one possible embodiment, in the above-described thermal management refrigerant module, when viewed along the width direction, the rectangular projected area of ​​the refrigerant channel block formed by the maximum dimensions in the length direction and the height direction is larger than the rectangular projected area of ​​the third heat exchanger, but does not exceed 2.7 times the rectangular projected area of ​​the third heat exchanger.

[0047] According to this structure, by reducing the dimensions of the refrigerant flow channel block in the length and height directions, the required configuration space for the thermal management refrigerant module in the length and height directions can be reduced.

[0048] Effects of the utility model

[0049] According to this utility model, a refrigerant flow channel block with small required configuration space and high adaptability, and a thermal management refrigerant module having such a refrigerant flow channel block can be provided. Attached Figure Description

[0050] Figure 1 This is a perspective view of a thermal management refrigerant module having a refrigerant flow channel block according to the first embodiment.

[0051] Figure 2 This is an exploded perspective view of the thermal management refrigerant module having the refrigerant flow channel block of the first embodiment.

[0052] Figure 3 This is a perspective view of the refrigerant flow channel block according to the first embodiment.

[0053] Figure 4 This is a diagram showing the refrigerant flow channel block of the first embodiment viewed from the width direction.

[0054] Figure 5 This is a schematic diagram showing the internal flow channel structure of the refrigerant flow channel block in the first embodiment.

[0055] Figure 6 This is a schematic diagram showing the refrigerant flow path including the thermal management refrigerant module involved in the first embodiment, illustrating the refrigerant flow in the cooling mode.

[0056] Figure 7 This is a schematic diagram showing the refrigerant flow path including the thermal management refrigerant module involved in the first embodiment, illustrating the refrigerant flow in a standalone cooling mode.

[0057] Figure 8 This is a schematic diagram showing the refrigerant flow path of the refrigerant module including the thermal management refrigerant module according to the first embodiment, showing the refrigerant flow in the heating mode.

[0058] Figure 9 This is a perspective view of a thermal management refrigerant module having a refrigerant flow channel block according to the second embodiment.

[0059] Figure 10 This is an exploded perspective view of the thermal management refrigerant module having the refrigerant flow channel block of the second embodiment.

[0060] Figure 11 This is a perspective view of the refrigerant flow channel block according to the second embodiment.

[0061] Figure 12 This is a diagram showing the refrigerant flow channel block of the second embodiment viewed from the width direction.

[0062] Figure 13 This is a schematic diagram showing the internal flow channel structure of the refrigerant flow channel block in the second embodiment.

[0063] Figure 14 This is a schematic diagram showing the refrigerant flow path including the thermal management refrigerant module involved in the second embodiment, illustrating the refrigerant flow in the cooling mode.

[0064] Figure 15 This is a schematic diagram showing the refrigerant flow path including the thermal management refrigerant module involved in the second embodiment, illustrating the refrigerant flow in a standalone cooling mode.

[0065] Figure 16 This is a schematic diagram showing the refrigerant flow path including the thermal management refrigerant module involved in the second embodiment, illustrating the refrigerant flow in heating mode.

[0066] Figure 17 This is a perspective view of the refrigerant flow channel block of a modified embodiment of the second embodiment.

[0067] Figure 18 This is a schematic diagram showing the internal flow channel structure of the refrigerant flow channel block in a modified example of the second embodiment.

[0068] Figure 19 This is a perspective view of a thermal management refrigerant module that utilizes this modified refrigerant flow channel block.

[0069] Symbol explanation:

[0070] 1, 2, 2A… Thermal management refrigerant module; 100, 200, 200A… Refrigerant flow channel block; 10… First heat exchanger; 11… Refrigerant inlet port; 12… Refrigerant outlet port; 20… Second heat exchanger; 30… Third heat exchanger; 31… Low-temperature side refrigerant inlet port; 40… Evaporator; 50… Liquid receiver; 60… Compressor; 70… Mounting section; 81… First valve mounting port; 82… Second valve mounting port; 91… First sensor mounting port; 92… Second sensor mounting port; 93… Third sensor mounting port; 101, 201… First outer surface; 102, 202… Second outer surface; 103, 203… Third outer surface; 104, 204… Fourth outer surface; 105, 205… Fifth outer surface; 106, 206… Sixth outer surface; 109, 209… Air tank; 110… 210…First flow channel, 120, 220…Second flow channel, 130, 230…Third flow channel, 140, 240…Fourth flow channel, 150, 250…Fifth flow channel, 160, 260…Sixth flow channel, 170, 270…Seventh flow channel, 180, 280…Eighth flow channel, 190, 290…Ninth flow channel, CV…One-way valve, J, J'…Connecting connector, P1, P1'…First port, P2, P2'…Second port, P3, P3'…Third port, D1…Length direction, D2…Height direction, D3…Width direction, P4, P4'…Fourth port, P5, P5'…Fifth port, P6, P6'…Sixth port, P7'…Seventh port, P8'…Eighth port, S1…First sensor, S2…Second sensor, S3…Third sensor, V1…First expansion valve, V2…Second expansion valve. Detailed Implementation

[0071] Hereinafter, various embodiments of the present invention will be described with reference to the accompanying drawings. The specific embodiments described below are only for illustrating the structure that the present invention can adopt, and are not intended to limit it. In each embodiment, the same or similar elements are sometimes labeled with the same reference numerals and repeated descriptions are omitted.

[0072] It should be understood that the terms "first," "second," and similar terms used in this utility model do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Directional terms such as "front / back," "up / down," and / or "left / right" are defined based on the drawing orientation of the corresponding accompanying drawings for ease of explanation and are not intended to limit position or spatial orientation.

[0073] <First Implementation Method>

[0074] The following is for reference Figures 1 to 8 This describes the refrigerant flow channel block 100 and the thermal management refrigerant module 1 equipped with the refrigerant flow channel block 100 in the first embodiment of the present invention. Figure 1 , Figure 2 These are a 3D view and an exploded 3D view of the thermal management refrigerant module 1. Figure 3 This is a three-dimensional view of the refrigerant flow channel block 100. Figure 4 This is a diagram showing the refrigerant flow channel block 100 viewed along the width direction D3. Figure 5 This is a schematic diagram showing the internal flow channel structure of the refrigerant flow channel block 100, with the extension direction of the refrigerant flow channel shown by dashed lines. Figures 6-8 This is a schematic diagram showing the overall refrigerant flow path circulation, including the thermal management refrigerant module 1. Figures 6-8 The arrows indicate refrigerant flow in cooling mode, standalone cooling mode, and heating mode, respectively. Additionally, the parts outside of thermal management refrigerant module 1... Figures 6-8 The area is outlined with a dashed line.

[0075] The thermal management refrigerant module 1 includes a refrigerant flow channel block 100, a first heat exchanger 10, a second heat exchanger 20, an evaporator 40, a liquid receiver 50, valves, and sensors. The valves include, for example, a first expansion valve V1 and a second expansion valve V2. The first expansion valve V1 and the second expansion valve V2 can be electronic expansion valves or mechanical expansion valves. The sensors are used to detect the temperature and / or pressure of the refrigerant flowing through the refrigerant flow channel, and include, for example, a first sensor S1, a second sensor S2, and a third sensor S3. The thermal management refrigerant module 1, together with the compressor 60, constitutes the refrigerant circulation path.

[0076] First, the refrigerant flow channel block 100 will be described. For ease of explanation, it will be... Figure 4 The left and right directions are defined as the length direction D1 of the refrigerant flow channel block 100, the up and down directions are defined as the height direction D2 of the refrigerant flow channel block 100, and the inward and outward directions are defined as the width direction D3 of the refrigerant flow channel block 100.

[0077] The refrigerant flow channel block 100 is a cylindrical shape with approximately the same dimensions in the length direction D1, height direction D2, and width direction D3. Specifically, the ratio of the maximum dimensions of the refrigerant flow channel block 100 in the length direction D1, height direction D2, and width direction D3 is in the range of 1:0.8 to 1.2:0.8 to 1.2, preferably 1:0.85:1.12. By setting the refrigerant flow channel block 100 as a cylindrical shape with similar maximum dimensions in the length, width, and height directions, the required configuration space for the refrigerant flow channel block 100 can be minimized, thereby increasing the overall design freedom of the thermal management refrigerant module 1. Moreover, the approximately cylindrical structure makes it possible to install valves on various surfaces of the refrigerant flow channel block 100, thus allowing for flexible design of valve installation positions according to the configuration requirements of different vehicle models. Compared with existing plate-shaped flow channel plates, this design improves the adaptability of the refrigerant flow channel block 100 to different vehicle models and reduces manufacturing costs.

[0078] Furthermore, when viewed along the length direction D1, the rectangular projected area of ​​the refrigerant channel block 100, formed by the maximum dimensions in the height direction D2 and the width direction D3, is larger than the rectangular projected areas of the first heat exchanger 10 and the second heat exchanger 20, but does not exceed 2.3 times the rectangular projected areas of the first heat exchanger 10 and the second heat exchanger 20. By reducing the dimensions of the refrigerant channel block 100 in the height direction D2 and the width direction D3, the required configuration space of the thermal management refrigerant module 1 in the height and width directions can be reduced.

[0079] The refrigerant flow channel block 100 has a first outer surface 101 and a second outer surface 102 opposite each other in the length direction D1, a third outer surface 103 and a fourth outer surface 104 opposite each other in the height direction D2, and a fifth outer surface 105 and a sixth outer surface 106 opposite each other in the width direction D3. It should be noted that surfaces of the refrigerant flow channel block 100 facing the same direction belong to the same outer surface; for example, all faces of the refrigerant flow channel block 100... Figure 4 The outer surface on the right side of the refrigerant channel block 100 is the first outer surface 101. Ports for refrigerant to flow into / out of the refrigerant channel are provided on the outer surface of the refrigerant channel block 100. Multiple refrigerant channels for refrigerant flow are formed inside the refrigerant channel block 100. The refrigerant channel block 100 is integrally formed. Here, "integral forming" means forming a single component by processing a single piece of material. Because the refrigerant channel block 100 is integrally formed and refrigerant channels are formed internally, compared to a split structure formed by multiple parts, it can improve sealing performance and prevent refrigerant leakage.

[0080] Specifically, a first port P1 is provided on the first outer surface 101, a second port P2 and a third port P3 are provided on the second outer surface 102, and a fourth port P4, a fifth port P5, and a sixth port P6 are provided on the fifth outer surface 105. The first port P1 to the third port P3 allow refrigerant to directly enter and exit the refrigerant channel block 100 from the first heat exchanger 10 or the second heat exchanger 20. "Direct entry and exit" here means that the refrigerant flows directly from the heat exchanger into the refrigerant channel block 100 without passing through other pipes or connectors, or flows directly from the refrigerant channel block 100 to the heat exchanger. The multiple refrigerant channels include at least a first channel 110, a second channel 120, and a third channel 130 extending along the length direction D1; a fourth channel 140 and a fifth channel 150 extending along the height direction D2; and a sixth channel 160 and a seventh channel 170 extending along the width direction D3. By utilizing these three-dimensional refrigerant channels extending in three intersecting directions, the length of the refrigerant channels can be shortened, the overall volume of the refrigerant channel block 100 can be reduced, and the pressure loss and heat loss within the refrigerant channel block 100 can be decreased. Furthermore, due to the shortened length of the refrigerant channels, the risk of oil accumulation can be reduced, and heat exchange efficiency can be improved. Moreover, by utilizing the fourth channel 140 and the fifth channel 150 extending along the height direction D2, the refrigerant can flow vertically, further reducing the risk of oil accumulation.

[0081] The first flow channel 110 is connected to the first port P1, and via the first port P1, it is connected to the refrigerant outlet port 12 of the first heat exchanger 10. The second flow channel 120 is connected to the second port P2, and via the second port P2, it is connected to the refrigerant inlet port (not shown) of the second heat exchanger 20. The third flow channel 130 is connected to the third port P3, and via the third port P3, it is connected to the refrigerant outlet port (not shown) of the second heat exchanger 20. The fourth flow channel 140 connects the first flow channel 110 and the second flow channel 120. The fifth flow channel 150 connects the third flow channel 130 and the seventh flow channel 170. The sixth flow channel 160 is connected to the fourth port P4, and via the fourth port P4, it is connected to the refrigerant inlet port of the evaporator 40. A one-way valve CV is provided in the fifth flow channel 150 to restrict the flow direction of the refrigerant. The seventh flow channel 170 is connected to the fifth port P5, and via the fifth port P5, it is connected to the refrigerant outlet port (not shown) of the evaporator 40. The refrigerant flowing from the seventh channel 170 merges with the refrigerant flowing from the third channel 130 in the fifth channel 150. An eighth channel 180 is also formed inside the refrigerant channel block 100, which connects the sixth channel 160 and the first channel 110. The refrigerant flowing from the first channel 110 branches into the fourth channel 140 and the eighth channel 180. By utilizing the multiple channels extending in different directions within the refrigerant channel block 100, the thermal management refrigerant module 1 can be configured to connect the second heat exchanger 20 and the evaporator 40 in parallel.

[0082] Furthermore, the refrigerant flow channel block 100 also has a ninth flow channel 190, which is connected to the sixth port P6 and connected to the refrigerant inlet port of the compressor 60 via the sixth port P6. The ninth flow channel 190 is connected to the fifth flow channel 150, and the refrigerant that merges in the fifth flow channel 150 flows to the compressor 60 via the ninth flow channel 190.

[0083] Furthermore, the refrigerant outlet port of the compressor 60 is connected to the refrigerant inlet port 11 of the first heat exchanger 10 via a connecting connector J, thereby allowing the refrigerant flowing from the compressor 60 to flow into the first heat exchanger 10 through the flow channel inside the connecting connector J. In this embodiment, the connecting connector J is a separate unit from the refrigerant flow channel block 100, but it can also be fixed to the refrigerant flow channel block 100 by welding or other methods.

[0084] Multiple mounting portions 70 for direct mounting of heat exchangers are provided on the first outer surface 101 and the second outer surface 102, respectively. The first heat exchanger 10 and the second heat exchanger 20 are directly fixed to the first outer surface 101 and the second outer surface 102 of the refrigerant channel block 100 through their respective mounting portions 70. This allows two heat exchangers to be arranged on opposite outer surfaces of the refrigerant channel block 100, thus simplifying and shortening the refrigerant channel, reducing heat loss and pressure loss. Here, "direct mounting" and "direct fixing" refer to the heat exchanger being mounted and fixed to the refrigerant channel block 100 in a manner where its outer surface is in contact with the outer surface of the refrigerant channel block 100 (where "in contact" means the distance between the outer surface of the heat exchanger facing the refrigerant channel block 100 and the plane containing the port of the refrigerant channel of the refrigerant channel block 100 does not exceed 4 cm), without the need for other pipes or connectors. Since the first heat exchanger 10 and the second heat exchanger 20 are directly installed on the refrigerant flow channel block 100, additional connecting pipes can be omitted, reducing manufacturing costs, reducing the configuration space of the thermal management refrigerant module 1, and further preventing refrigerant leakage.

[0085] A first valve mounting port 81 and a second valve mounting port 82 are provided on the third outer surface 103, where no heat exchanger is located. These two ports are for inserting valves into the refrigerant flow path. A first expansion valve V1 is inserted through the first valve mounting port 81 into the third outer surface 103 and then into the sixth flow path 160. A second expansion valve V2 is inserted through the second valve mounting port 82 into the third outer surface 103 and then into the second flow path 120. Thus, in the refrigerant flow path block 100, the first expansion valve V1 and the second expansion valve V2 can be used to throttle the refrigerant flowing to the evaporator 40 and the second heat exchanger 20, respectively, thereby facilitating easy switching of the operating modes described later. Furthermore, since the heat exchanger and valves are not located on the same side of the refrigerant flow path block 100, the length of a single side of the refrigerant flow path block 100 can be reduced. This allows for a reduction in the size of the thermal management refrigerant module 1 in a single direction.

[0086] As mentioned above, the surfaces of the refrigerant flow channel block 100 facing the same direction belong to the same outer surface. That is, the same outer surface can have multiple surfaces facing the same direction but not on the same plane. In this embodiment, the first valve mounting port 81 and the second valve mounting port 82 are both provided on the third outer surface 103, but not on the same plane. In this way, the length of the refrigerant flow path can be shortened and the volume of the refrigerant flow channel block 100 can be reduced.

[0087] Additionally, a first sensor mounting port 91 is provided on the third outer surface 103, and a second sensor mounting port 92 and a third sensor mounting port 93 are provided on the fifth outer surface 105. The first sensor mounting ports 91 to 93 are sensor mounting ports for inserting sensors into the refrigerant flow channels. The first sensor S1 is inserted into the seventh flow channel 170 from the third outer surface 103 via the first sensor mounting port 91 to detect the temperature and pressure of the refrigerant flowing out of the evaporator 40. The second sensor S2 is inserted into the third flow channel 130 from the fifth outer surface 105 via the second sensor mounting port 92 to detect the temperature and pressure of the refrigerant flowing out of the second heat exchanger 20. The third sensor S3 is inserted into the eighth flow channel 180 from the fifth outer surface 105 via the third sensor mounting port 93 to detect the temperature and pressure of the refrigerant flowing out of the first heat exchanger 10 and towards the evaporator 40.

[0088] In this embodiment, the first sensor mounting port 91, the first valve mounting port 81, and the second valve mounting port 82 are all located on the third outer surface 103, but not on the same plane. This shortens the length of the refrigerant flow path and reduces the volume of the refrigerant flow channel block 100.

[0089] In this embodiment, the first valve mounting port 81, the second valve mounting port 82, the first sensor mounting port 91, the second sensor mounting port 92, and the third sensor mounting port 93 can be respectively set on different outer surfaces and planes, which makes the setting position of the valve and sensor more free and flexible and can be adapted to different vehicle models.

[0090] Furthermore, to prevent heat loss caused by close proximity between low-temperature regions flowing with low-temperature refrigerant and high-temperature regions flowing with high-temperature refrigerant, the refrigerant channel block 100 has an air groove 109 extending along the height direction D2 on its fifth outer surface 105. This air groove 109 is recessed to an appropriate depth from the fifth outer surface 105 toward the sixth outer surface 106 along the width direction D3. Specifically, when viewed from the width direction D3, two air grooves 109 are provided between the fifth channel 150 and the sixth channel 160 and the eighth channel 180 of the refrigerant channel block 100. By using these air grooves 109 to insulate the sixth channel 160 and the eighth channel 180, which are high-temperature regions, and the fifth channel 150, which is a low-temperature region, heat loss caused by heat conduction in the refrigerant channel block 100 can be effectively avoided.

[0091] The following describes the operating modes of the thermal management refrigerant module 1.

[0092] When the thermal management refrigerant module 1 is applied to a vehicle, it can switch between a standalone cooling mode, a cooling-cooling mode, and a heating mode. The standalone cooling mode cools the air inside the vehicle's cabin; the cooling-cooling mode cools both the air inside the cabin and heat-generating devices such as batteries; and the heating mode heats the air inside the cabin. The first heat exchanger 10 is, for example, a water-cooled condenser that allows heat exchange between the refrigerant and the coolant outside the thermal management refrigerant module 1. The second heat exchanger 20 is, for example, a cooler that, in the cooling-cooling mode, allows heat exchange between the coolant cooling the heat-generating devices and the refrigerant; and in the heating mode, allows heat exchange between the coolant absorbing heat from the environment and the refrigerant.

[0093] In cooling mode, such as Figure 6 As shown, the first expansion valve V1 and the second expansion valve V2 are set to throttling mode. The compressor 60 operates, compressing the refrigerant to the first heat exchanger 10. The refrigerant dissipates heat from the coolant in the first heat exchanger 10, while the resistance heater on the coolant side is off. The refrigerant flowing out of the first heat exchanger 10 is split after passing through the receiver 50. A portion of the refrigerant flows into the evaporator 40 after being throttled by the first expansion valve V1, where it absorbs heat from the vehicle interior to cool the air inside the vehicle, and then flows to the one-way valve CV. The other portion of the refrigerant flows into the second heat exchanger 20 after being throttled by the second expansion valve V2, where it absorbs heat from the coolant to cool the battery, and then merges with the refrigerant flowing out of the evaporator 40 and flows into the compressor 60. Thus, the refrigerant completes one cycle.

[0094] In standalone cooling mode, such as Figure 7 As shown, the first expansion valve V1 is set to a throttling state, and the second expansion valve V2 is closed. The compressor 60 operates, pressing the refrigerant to the first heat exchanger 10. The refrigerant dissipates heat to the coolant in the first heat exchanger 10, and the resistance heater on the coolant side is off. Because the second expansion valve V2 is closed, the refrigerant flowing from the first heat exchanger 10 flows into the evaporator 40 after being throttled only by the first expansion valve V1. In the evaporator 40, it absorbs heat from the vehicle interior to cool the air inside the vehicle. Afterward, it flows to the one-way valve CV, and the refrigerant after passing through the one-way valve CV flows into the compressor 60. Thus, the refrigerant completes one cycle.

[0095] In heating mode, such as Figure 8As shown, the first expansion valve V1 is closed, and the second expansion valve V2 is set to a throttling state. The compressor 60 operates, compressing the refrigerant to the first heat exchanger 10, where the refrigerant dissipates heat to the coolant. At this time, the resistance heater on the coolant side is activated (ON), and the coolant absorbs heat and is further heated by the resistance heater, then dissipates heat to the cabin air through other components for heating. Because the first expansion valve V1 is closed, the refrigerant flowing from the first heat exchanger 10 only flows into the second heat exchanger 20 after being throttled by the second expansion valve V2. In this mode, the coolant in the outdoor low-temperature heat exchanger absorbs heat from the outside air and then dissipates heat to the refrigerant in the second heat exchanger 20; that is, the refrigerant absorbs heat in the second heat exchanger 20 and then flows into the compressor 60. Thus, the refrigerant completes one cycle.

[0096] Therefore, by using the first expansion valve V1 and the second expansion valve V2, it is possible to easily switch between individual cooling mode, cooling-cooling mode and heating mode.

[0097] <Second Implementation Method>

[0098] The following is for reference Figures 9-16 This describes the refrigerant flow channel block 200 and the thermal management refrigerant module 2 equipped with the refrigerant flow channel block 200 in the second embodiment of the present invention. Figure 9 , Figure 10 These are a 3D view and an exploded 3D view of the thermal management refrigerant module 2. Figure 11 This is a three-dimensional view of the refrigerant flow channel block 200. Figure 12 This is a diagram showing the refrigerant flow channel block 200 viewed from the width direction D3. Figure 13 This is a schematic diagram showing the internal flow channel structure of the refrigerant flow channel block 200, with the extension direction of the refrigerant flow channel shown by dashed lines. Figures 14-16 This is a schematic diagram showing the overall refrigerant flow path circulation, including the thermal management refrigerant module 2. Figures 14-16 The arrows indicate refrigerant flow in cooling mode, standalone cooling mode, and heating mode, respectively. Additionally, the parts outside of thermal management refrigerant module 2... Figures 14-16 The area is outlined with a dashed line.

[0099] The thermal management refrigerant module 2 includes a refrigerant flow channel block 200 instead of the refrigerant flow channel block 100, and also includes a third heat exchanger 30. In this embodiment, the third heat exchanger 30 is, for example, an intermediate heat exchanger that allows a relatively high-temperature refrigerant to exchange heat with a relatively low-temperature refrigerant. Other components are the same as those in the thermal management refrigerant module 1. The following mainly describes the differences between the second embodiment and the first embodiment; identical parts are labeled with the same symbols and detailed descriptions are omitted.

[0100] like Figure 11As shown, the refrigerant channel block 200 has dimensions in the length direction D1, height direction D2, and width direction D3. The refrigerant channel block 200 in the second embodiment is also a cylindrical shape with approximately the same dimensions in the length direction D1, height direction D2, and width direction D3. Furthermore, when viewed along the width direction D3, the rectangular projected area formed by the maximum dimensions of the refrigerant channel block 200 in the length direction D1 and height direction D2 is larger than the rectangular projected area of ​​the third heat exchanger 30, but does not exceed 2.7 times the rectangular projected area of ​​the third heat exchanger 30. By reducing the dimensions of the refrigerant channel block 200 in the length direction D1 and height direction D2, the required configuration space for the thermal management refrigerant module 2 in the length and height directions can be reduced.

[0101] The refrigerant flow channel block 200 has a first outer surface 201 and a second outer surface 202 facing each other in the length direction D1, a third outer surface 203 and a fourth outer surface 204 facing each other in the height direction D2, and a fifth outer surface 205 and a sixth outer surface 206 facing each other in the width direction D3. The orientation of the first outer surface 201 to the sixth outer surface 206 is the same as that of the first outer surface 101 to the sixth outer surface 106 in the first embodiment.

[0102] Multiple mounting portions 70 for directly mounting heat exchangers are provided on the first outer surface 201, the second outer surface 202, and the fifth outer surface 205. The first heat exchanger 10 and the second heat exchanger are directly fixed to the first outer surface 201 and the second outer surface 202 of the refrigerant flow channel block 200 via the mounting portions 70. The third heat exchanger 30 is directly fixed to the third outer surface 203 via the mounting portion 70. Thus, the thermal management refrigerant module 2 can be configured in a T-shape with the first heat exchanger 10 and the second heat exchanger 20 arranged opposite each other, and the third heat exchanger 30 arranged adjacent to the first heat exchanger 10 and the second heat exchanger 20. Therefore, while further improving heat exchange performance, the thermal management refrigerant module 2 can be made more compact, reducing the required configuration space.

[0103] The refrigerant flow channel block 200 has ports on its outer surface for refrigerant to flow into / out of the refrigerant flow channel. Multiple refrigerant flow channels are formed inside the refrigerant flow channel block 200 for refrigerant to flow through.

[0104] Specifically, a first port P1' is provided on the first outer surface 201, a second port P2' and a third port P3' are provided on the second outer surface 202, and a fourth port P4', a fifth port P5', a sixth port P6', a seventh port P7', and an eighth port P8' are provided on the fifth outer surface 205. The first port P1' to the third port P3' allow refrigerant to directly enter and exit the refrigerant channel in the refrigerant channel block 200 from the first heat exchanger 10 or the second heat exchanger 20. The fourth port P4', the fifth port P5', and the seventh port P7' allow refrigerant to directly enter and exit the refrigerant channel in the refrigerant channel block 200 from the third heat exchanger 30. The multiple refrigerant flow channels include at least a first flow channel 210, a second flow channel 220 and a third flow channel 230 extending along the length direction D1, a fourth flow channel 240 and a fifth flow channel 250 extending along the height direction D2, and a sixth flow channel 260 and a seventh flow channel 270 extending along the width direction D3.

[0105] The first flow channel 210 is connected to the first port P1' and is connected to the refrigerant outlet port 12 of the first heat exchanger 10 via the first port P1'. The second flow channel 220 is connected to the second port P2' and is connected to the refrigerant inlet port (not shown) of the second heat exchanger 20 via the second port P2'. The third flow channel 230 is connected to the third port P3' and is connected to the refrigerant outlet port (not shown) of the second heat exchanger 20 via the third port P3'. The fourth flow channel 240 connects the first flow channel 210 and the second flow channel 220. The fifth flow channel 250 connects the third flow channel 230 and the seventh flow channel 270. The sixth flow channel 260 is connected to the fourth port P4' and is connected to the high-temperature side refrigerant inlet port (not shown) of the third heat exchanger 30 via the fourth port P4'. In addition, the refrigerant flowing out of the first flow channel 210 branches into the fourth flow channel 240 and the sixth flow channel 260. The seventh flow channel 270 is connected to the fifth port P5', and via the fifth port P5', it is connected to the low-temperature refrigerant outlet port (not shown) of the third heat exchanger 30. Additionally, the refrigerant flowing from the seventh flow channel 270 merges with the refrigerant flowing from the third flow channel 230 in the fifth flow channel 250. An eighth flow channel 280 is also formed inside the refrigerant flow channel block 200. One end of the eighth flow channel 280 is connected to the sixth port P6', and via the sixth port P6', it is connected to the refrigerant inlet port (not shown) of the evaporator 40. The other end of the eighth flow channel 280 is connected to the seventh port P7', and via the seventh port P7', it is connected to the high-temperature refrigerant outlet port (not shown) of the third heat exchanger 30. Although not shown in the accompanying drawings, the refrigerant outlet port of the evaporator 40 is connected to the low-temperature refrigerant inlet port 31 of the third heat exchanger 30 outside the refrigerant flow channel block 200.

[0106] Furthermore, the refrigerant flow channel block 200 also has a ninth flow channel 290, which is connected to the eighth port P8' and connected to the refrigerant inlet port of the compressor 60 via the eighth port P8'. The ninth flow channel 290 is connected to the fifth flow channel 250, and the refrigerant that merges in the fifth flow channel 250 flows to the compressor 60 via the ninth flow channel 290.

[0107] In addition, the refrigerant outlet port of the compressor 60 is connected to the refrigerant inlet port 11 of the first heat exchanger 10 via a connecting connector J', thereby allowing the refrigerant flowing out of the compressor 60 to flow into the first heat exchanger 10 through the flow channel inside the connecting connector J'.

[0108] A first valve mounting port 81 and a second valve mounting port 82 are provided on the third outer surface 203, where no heat exchanger is located. A first expansion valve V1 is inserted into the third outer surface 203 through the first valve mounting port 81 and then into the eighth flow channel 280. A second expansion valve V2 is inserted into the third outer surface 203 through the second valve mounting port 82 and then into the second flow channel 220. Thus, similar to the refrigerant flow channel block 100, the refrigerant flow channel block 200 can also throttle the refrigerant flowing to the evaporator 40 and the second heat exchanger 20 using the first expansion valve V1 and the second expansion valve V2, respectively. This allows for switching between different operating modes.

[0109] As mentioned above, the surfaces of the refrigerant flow channel block 200 facing the same direction belong to the same outer surface. That is, the same outer surface may have multiple surfaces facing the same direction but not on the same plane.

[0110] In this embodiment, the first sensor mounting port 91 is disposed on the third outer surface 203, and the second sensor mounting port 92 and the third sensor mounting port 93 are disposed on the fourth outer surface 204. The first sensor S1 is inserted into the seventh flow channel 270 from the third outer surface 203 via the first sensor mounting port 91. The second sensor S2 is inserted into the third flow channel 230 from the fourth outer surface 204 via the second sensor mounting port 92. The third sensor S3 is inserted into the sixth flow channel 260 from the fourth outer surface 204 via the third sensor mounting port 93. Although the physical parameters detected by the first sensor S1 to the third sensor S3 are the same as in the first embodiment, the third sensor S3 detects the temperature and pressure of the refrigerant flowing out of the first heat exchanger 10 and into the evaporator 40 at a position between the refrigerant flow path from the first heat exchanger 10 to the third heat exchanger 30.

[0111] In this embodiment, both the first valve mounting port 81 and the second valve mounting port 82 are located on the third outer surface 203, but not on the same plane. This shortens the length of the refrigerant flow path and reduces the volume of the refrigerant flow channel block 200.

[0112] In this embodiment, the first valve mounting port 81, the second valve mounting port 82, the first sensor mounting port 91, the second sensor mounting port 92, and the third sensor mounting port 93 can be respectively set on different outer surfaces and planes, which makes the setting position of the valve and sensor more free and flexible and can be adapted to different vehicle models.

[0113] Furthermore, the refrigerant channel block 200 has an air groove 209 extending along the height direction D2 on its fifth outer surface 205, and this air groove 209 is recessed to an appropriate depth from the fifth outer surface 205 toward the sixth outer surface 206 along the width direction D3. Specifically, when viewed from the width direction D3, two air grooves 209 are provided in the region between the fifth channel 250 and the sixth channel 260 and the eighth channel 280 of the refrigerant channel block 200. These air grooves 209 are used to insulate the high-temperature and low-temperature regions of the refrigerant channel block 200, particularly the high-temperature and low-temperature side channels of the third heat exchanger 30.

[0114] The refrigerant flow channel block 200 and the thermal management refrigerant module 2 with the above structure can achieve the same technical effects as the refrigerant flow channel block 100 and the thermal management refrigerant module 1 of the first embodiment.

[0115] The types of operating modes and the switching between operating modes of the thermal management refrigerant module 2 are the same as in the first embodiment, and their descriptions are omitted here. However, since a third heat exchanger 30 is added compared to the first embodiment, in both the standalone cooling mode and the cooling-cooling mode, the refrigerant flowing from the first heat exchanger 10 to the evaporator 40 flows through the high-temperature side region inside the third heat exchanger 30 before passing through the first expansion valve V1. Furthermore, the refrigerant flowing out of the evaporator 40 flows through the low-temperature side region inside the third heat exchanger 30 before flowing towards the one-way valve CV. As a result, the heat exchange efficiency of the thermal management refrigerant module 2 can be improved without changing the operating mode.

[0116] <Modifications of the Second Embodiment>

[0117] See Figures 17-19 A variation of the second embodiment will be described. Figure 17 This is a perspective view of the refrigerant flow channel block 200A in this modified example. Figure 18 This is a schematic diagram showing the internal flow channel structure of the refrigerant flow channel block 200A. The extension direction of the refrigerant flow channel is shown by dashed lines. Figure 19This is a perspective view of the thermal management refrigerant module 2A that utilizes the refrigerant flow channel block 200A. In this modified example, the main difference between the refrigerant flow channel block 200A and the refrigerant flow channel block 200 of the second embodiment described above lies in the placement of the sensors and valves. Other aspects are the same, and only the differences will be described below, omitting other details.

[0118] In the refrigerant flow channel block 200A, the first valve mounting port 81 and the second valve mounting port 82 are respectively located on the fourth outer surface 204 and the sixth outer surface 206, where no heat exchanger is provided. The first expansion valve V1 is inserted into the eighth flow channel 280 from the fourth outer surface 204 through the first valve mounting port 81, and the second expansion valve V2 is inserted into the second flow channel 220 from the sixth outer surface 206 through the second valve mounting port 82.

[0119] Additionally, the first sensor mounting port 91 and the third sensor mounting port 93 are disposed on the third outer surface 203, and the second sensor mounting port 92 is disposed on the fourth outer surface 204. The first sensor S1 is inserted into the seventh flow channel 270 through the first sensor mounting port 91 from the third outer surface 203. The second sensor S2 is inserted into the third flow channel 230 through the second sensor mounting port 92 from the fourth outer surface 204. The third sensor S3 is inserted into the sixth flow channel 260 through the third sensor mounting port 93 from the third outer surface 203.

[0120] In this embodiment, the first valve mounting port 81, the second valve mounting port 82, the first sensor mounting port 91, the second sensor mounting port 92, and the third sensor mounting port 93 can be respectively set on different outer surfaces and planes, which makes the setting position of the valve and sensor more free and flexible and can be adapted to different vehicle models.

[0121] In addition to achieving the same technical effects as the refrigerant flow channel block 200, the refrigerant flow channel block 200A with the above structure can also design the valve configuration position according to actual needs, improve the configuration freedom of the valve, and further improve the adaptability of the thermal management refrigerant module 2A to different vehicle models.

[0122] <Other variations>

[0123] The embodiments of this utility model have been described above, but this utility model is not limited to these examples. Those skilled in the art can appropriately add, remove, or modify the constituent elements of the above embodiments, or appropriately combine some features of the embodiments, as long as they do not violate the spirit of this utility model, and such modifications are included within the scope of this utility model.

[0124] In the above embodiment, mounting portions for mounting heat exchangers are provided on the first, second, and fifth outer surfaces of the refrigerant channel block. The first and second heat exchangers are disposed on the first and second outer surfaces of the refrigerant channel block, and the third heat exchanger is disposed on the fifth outer surface. However, this is not a limitation; mounting portions may be provided on at least two of the first to sixth outer surfaces. Since the heat exchangers can be arranged on opposite and / or adjacent outer surfaces of the refrigerant channel block, the length of the refrigerant channel can be shortened, reducing heat loss and pressure loss. Furthermore, this structure increases the flexibility of heat exchanger configuration, thereby improving the compatibility between the refrigerant channel block and the thermal management refrigerant module.

[0125] In the above embodiments, the valve is disposed on, for example, the third, fourth, or sixth outer surface, but the placement of the valve is not limited to these. As long as the outer surface is not used for mounting a heat exchanger, a valve mounting port can be provided for installing the valve. Since the valve can be installed on multiple outer surfaces of the refrigerant channel block in different orientations, not for heat exchanger placement, the placement of the valve is more flexible and the configuration freedom is increased, allowing for adaptation to different vehicle models. This further improves the compatibility of the refrigerant channel block and the thermal management refrigerant module.

[0126] In the above embodiments, the sensors are disposed on the third and fourth outer surfaces, but the sensor placement is not limited to these; the sensor can be disposed on any outer surface of the refrigerant flow channel block. Therefore, the sensor can be configured according to the available space or actual needs, thus enabling easy detection of refrigerant temperature and pressure while increasing the flexibility of sensor placement, allowing adaptation to different vehicle models. This further improves the compatibility of the refrigerant flow channel block and the thermal management refrigerant module.

[0127] In addition, in this embodiment, the number of valves and sensors are two and three respectively, but it is not limited to this, and the number of valves and sensors can be appropriately configured according to actual needs.

[0128] In the above embodiments, the sensor is used to detect the temperature and pressure of the refrigerant, but it can also detect only either temperature or pressure. Other physical parameters of the refrigerant can also be detected as needed.

[0129] In the above embodiments, the first heat exchanger is a water-cooled condenser, the second heat exchanger is a cooler, and the third heat exchanger is an intermediate heat exchanger. However, the type of heat exchanger is not limited to this, and other known heat exchangers may also be used.

[0130] In the above embodiment, the number of air slots is two, but the number of air slots is not limited to this; it can be one or more. Furthermore, in the above embodiment, the air slot is a non-through slot recessed to an appropriate depth from the fifth outer surface, but it is not limited to this; the air slot can also be a through slot extending from the fifth outer surface to the sixth outer surface.

Claims

1. A refrigerant flow channel block, characterized in that, The refrigerant flow channel block is integrally formed, and multiple refrigerant flow channels are formed inside for refrigerant flow. The refrigerant flow channel block has: a first outer surface and a second outer surface opposite each other in the length direction; a third outer surface and a fourth outer surface opposite each other in the height direction; and a fifth outer surface and a sixth outer surface opposite each other in the width direction. Ports are respectively provided on at least two of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface. The port allows refrigerant to directly enter and exit the refrigerant channel within the refrigerant channel block from the heat exchanger. A valve mounting port for inserting a valve into the refrigerant flow channel is provided on at least one of the following outer surfaces: the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface, excluding the at least two outer surfaces.

2. The refrigerant flow channel block according to claim 1, characterized in that, The plurality of refrigerant channels include at least refrigerant channels extending along the length direction, width direction, and height direction, respectively.

3. The refrigerant flow channel block according to claim 2, characterized in that, The at least two outer surfaces on which the port is provided include a first outer surface and a second outer surface.

4. The refrigerant flow channel block according to claim 3, characterized in that, The at least two outer surfaces on which the ports are provided also include the fifth outer surface.

5. The refrigerant flow channel block according to claim 1, characterized in that, A sensor mounting port for inserting a sensor into the refrigerant flow channel is provided on at least one of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface.

6. The refrigerant flow channel block according to any one of claims 1 to 5, characterized in that, The ratio of the maximum dimensions of the refrigerant flow channel block in the length direction, the width direction, and the height direction is 1:0.8 to 1.2:0.8:1.

2.

7. A thermal management refrigerant module, applied in a vehicle, characterized in that, It comprises: the refrigerant flow channel block according to claim 1, the first heat exchanger and the second heat exchanger serving as the heat exchanger, and the valve.

8. The thermal management refrigerant module according to claim 7, characterized in that, The refrigerant inlet port and / or refrigerant outlet port of each of the first and second heat exchangers, which allow refrigerant to enter and exit the refrigerant flow channel block, are directly connected to the port of the refrigerant flow channel block. The first heat exchanger and the second heat exchanger are directly mounted on the first outer surface and the second outer surface, respectively, and the valve is inserted into the third outer surface.

9. The thermal management refrigerant module according to claim 8, characterized in that, The thermal management refrigerant module also includes a third heat exchanger, which is directly mounted on the fifth outer surface. The refrigerant inlet and refrigerant outlet ports of each of the third heat exchangers are directly connected to the ports of the refrigerant flow channel block.

10. The thermal management refrigerant module according to claim 7, characterized in that, The thermal management refrigerant module also includes a sensor for detecting the temperature and / or pressure of the refrigerant flowing in the refrigerant channel. The sensor is inserted into at least one of the first outer surface, the second outer surface, the third outer surface, the fourth outer surface, the fifth outer surface, and the sixth outer surface of the refrigerant flow channel block.

11. The thermal management refrigerant module according to claim 8, characterized in that, The thermal management refrigerant module also includes an evaporator for evaporating the refrigerant. The refrigerant flow channels of the refrigerant flow channel block include a first flow channel, a second flow channel, and a third flow channel extending along the length direction; a fourth flow channel and a fifth flow channel extending along the height direction; a sixth flow channel and a seventh flow channel extending along the width direction; and an eighth flow channel. The first flow channel is connected to the refrigerant outlet port of the first heat exchanger. The second flow channel is connected to the refrigerant inlet port of the second heat exchanger. The third flow channel is connected to the refrigerant outlet port of the second heat exchanger. The fourth flow channel connects the first flow channel and the second flow channel. The fifth flow channel connects the third flow channel and the seventh flow channel. The sixth flow channel is connected to the refrigerant inlet port of the evaporator. The seventh flow channel is connected to the refrigerant outlet port of the evaporator, and the refrigerant flowing out from the seventh flow channel merges with the refrigerant flowing out from the third flow channel in the fifth flow channel. The eighth flow channel connects the sixth flow channel and the first flow channel, and the refrigerant flowing out of the first flow channel branches to the fourth flow channel and the eighth flow channel.

12. The thermal management refrigerant module according to claim 11, characterized in that, When viewed from the width direction, an air groove extending along the height direction is provided at the position between the fifth flow channel, the sixth flow channel, and the eighth flow channel of the refrigerant flow channel block.

13. The thermal management refrigerant module according to claim 11, characterized in that, The valve includes a first expansion valve and a second expansion valve. The first expansion valve is inserted into the sixth flow channel from the third outer surface, and the second expansion valve is inserted into the second flow channel from the third outer surface.

14. The thermal management refrigerant module according to claim 13, characterized in that, The thermal management refrigerant module can switch between a standalone cooling mode, a cooling-cooling mode, and a heating mode. The standalone cooling mode cools the air inside the vehicle's cabin, the cooling-cooling mode cools both the air inside the cabin and the heating devices, and the heating mode heats the air inside the cabin. In the standalone cooling mode, the first expansion valve is set to a throttling state, and the second expansion valve is closed. In the cooling mode, the first expansion valve and the second expansion valve are set to a throttling state. In the heating mode, the first expansion valve is closed and the second expansion valve is set to a throttling state.

15. The thermal management refrigerant module according to claim 9, characterized in that, The third heat exchanger is an intermediate heat exchanger that allows a relatively high-temperature refrigerant to exchange heat with a relatively low-temperature refrigerant. The thermal management refrigerant module also includes an evaporator for evaporating the refrigerant. The plurality of refrigerant channels include a first channel, a second channel, and a third channel extending along the length direction; a fourth channel and a fifth channel extending along the height direction; a sixth channel, a seventh channel, and an eighth channel extending along the width direction. The first flow channel is connected to the refrigerant outlet port of the first heat exchanger. The second flow channel is connected to the refrigerant inlet port of the second heat exchanger. The third flow channel is connected to the refrigerant outlet port of the second heat exchanger. The fourth flow channel connects the first flow channel and the second flow channel. The fifth flow channel connects the third flow channel and the seventh flow channel. The sixth flow channel is connected to the high-temperature refrigerant inlet port of the third heat exchanger, and the refrigerant flowing out of the first flow channel branches into the fourth and sixth flow channels. The seventh flow channel is connected to the low-temperature refrigerant outlet port of the third heat exchanger, and the refrigerant flowing out from the seventh flow channel merges with the refrigerant flowing out from the third flow channel in the fifth flow channel. One end of the eighth flow channel is connected to the refrigerant inlet port of the evaporator, and the other end is connected to the high-temperature side refrigerant outlet port of the third heat exchanger. The refrigerant outlet port of the evaporator is connected to the low-temperature refrigerant inlet port of the third heat exchanger.

16. The thermal management refrigerant module according to claim 15, characterized in that, The valve includes a first expansion valve and a second expansion valve. The first expansion valve is inserted into the eighth flow channel from the third outer surface, and the second expansion valve is inserted into the second flow channel from the third outer surface.

17. The thermal management refrigerant module according to claim 15, characterized in that, The valve includes a first expansion valve and a second expansion valve. The first expansion valve is inserted into the eighth flow channel from the fourth outer surface, and the second expansion valve is inserted into the second flow channel from the sixth outer surface.

18. The thermal management refrigerant module according to claim 8 or 9, characterized in that, When viewed along the length direction, the rectangular projected area of ​​the refrigerant channel block formed by the maximum dimensions in the width direction and the height direction is greater than the rectangular projected area of ​​the first heat exchanger and the second heat exchanger respectively, but does not exceed 2.3 times the rectangular projected area of ​​the first heat exchanger and the second heat exchanger respectively.

19. The thermal management refrigerant module according to claim 9, characterized in that, When viewed along the width direction, the rectangular projected area of ​​the refrigerant channel block formed by the maximum dimensions in the length and height directions is larger than the rectangular projected area of ​​the third heat exchanger, but does not exceed 2.7 times the rectangular projected area of ​​the third heat exchanger.

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