Heat Exchanger

Abstract

The present application relates to a heat exchanger, which is provided with a heat inlet collecting channel, a multi-layer heat circulation channel layer and a heat outlet collecting channel connected in sequence. The heat exchanger is also provided with a cold inlet collecting channel, a multi-layer cold circulation channel layer and a cold outlet collecting channel connected in sequence. The hot circulation channel layer is provided with a guide plate group extending along a direction perpendicular to a first preset direction, and the guide plate group is provided with a plurality of guide channels distributed along a direction perpendicular to the first preset direction. A first partition extending along a second preset direction is provided between the cold inlet collecting channel and the cold outlet collecting channel to divide the cold circulation channel layer into a first channel and a second channel, and a first notch is provided at one end of the first partition near the fourth end. The cold inlet collecting channel is provided on the side of the third end near the second end, and the cold outlet collecting channel is provided on the side of the third end near the first end. The heat exchanger provided by the present application solves the problem of low heat exchange efficiency of existing heat exchangers.

Description

Technical Field

[0001] The present application relates to the technical field of thermal management systems for new energy vehicles, and in particular to a heat exchanger. Background Art

[0002] Usually, in a heat exchanger, the channels where the coolant is located and the channels where the refrigerant is located are cross-layered, and in order to facilitate the installation of pipelines and to increase the heat exchange area of ​​the heat exchanger, the coolant inlet, coolant outlet, refrigerant inlet and refrigerant outlet are respectively located at the four corners of the heat exchanger. However, with such an arrangement, after the heat exchanger completes a heat exchange, the coolant temperature does not drop much, so the heat exchange efficiency of the existing heat exchanger is not high. Summary of the invention

[0003] Based on this, it is necessary to provide a heat exchanger to solve the problem of low heat exchange efficiency of existing heat exchangers.

[0004] The heat exchanger provided in the present application is provided with a heat inlet collecting channel, a plurality of heat cycle channel layers and a heat outlet collecting channel connected in sequence, and the heat exchanger is also provided with a cold inlet collecting channel, a plurality of cold cycle channel layers and a cold outlet collecting channel connected in sequence. The hot cycle channel layer and the cold cycle channel layer are cross-stacked so that heat can be transferred between adjacent hot cycle channel layers and cold cycle channel layers. The hot cycle channel layer includes a first end and a second end distributed along a first preset direction, the heat inlet collecting channel is arranged at the first end of the hot cycle channel layer, the heat outlet collecting channel is arranged at the second end of the hot cycle channel layer, and a guide plate group extending perpendicular to the first preset direction is provided between the first end and the second end of the hot cycle channel layer, and the guide plate group is provided with a plurality of guide channels distributed perpendicular to the first preset direction, so that the coolant can enter the heat outlet collecting channel from the heat inlet collecting channel through the plurality of guide channels. The cold circulation channel layer includes a third end and a fourth end distributed along a second preset direction, the cold flow inlet channel and the cold flow outlet channel are both arranged at the third end of the cold circulation channel layer, a first partition extending along the second preset direction is arranged between the cold flow inlet channel and the cold flow outlet channel to divide the cold circulation channel layer into a first channel and a second channel, and a first notch is arranged at one end of the first partition close to the fourth end, so that the refrigerant can enter the cold flow outlet channel from the cold flow inlet channel through the first channel, the first notch and the second channel in sequence. The angle between the first preset direction and the second preset direction is 70°-110°, and the cold flow inlet channel is arranged on the side of the third end close to the second end, and the cold flow outlet channel is arranged on the side of the third end close to the first end.

[0005] In one embodiment, the angle between the first preset direction and the second preset direction is 70°-110°.

[0006] In one embodiment, the guide plate group includes a second baffle extending perpendicular to the first preset direction, and two guide channels are respectively provided at both ends of the second baffle, and the coolant can enter the heat outlet collecting channel from the heat inlet collecting channel through the two guide channels. It can be understood that such a configuration effectively reduces the processing difficulty of the guide plate group, thereby reducing the manufacturing cost of the heat exchanger.

[0007] In one embodiment, the guide plate group includes a plurality of first guide plates distributed along a first preset direction, and one end of the first guide plate points to the heat inlet collector channel, and the other end is distributed in a divergent manner in a direction away from the heat inlet collector channel, and adjacent first guide plates are spaced apart to form a guide channel. It can be understood that such a configuration greatly improves the uniformity of the distribution of the coolant in the heat circulation channel layer, thereby further improving the heat exchange efficiency of the heat exchanger.

[0008] In one embodiment, the guide plate group includes a plurality of second guide plates distributed along a first preset direction, and adjacent second guide plates are spaced to form a guide channel, and the second guide plate includes a first guide section and a second guide section, one end of the first guide section points to the heat inlet collecting channel, and the other end is distributed in a divergent manner in a direction away from the heat inlet collecting channel, and the end of the second guide section away from the first guide section points to the heat outlet collecting channel, and the end of the second guide section close to the first guide section is distributed in a divergent manner in a direction away from the heat outlet collecting channel, and the end of the second guide section away from the first guide section is connected to the end of the first guide section away from the heat inlet collecting channel. It can be understood that such a configuration further improves the uniformity of the distribution of the coolant in the heat circulation channel layer, thereby further improving the heat exchange efficiency of the heat exchanger.

[0009] In one embodiment, the second guide vane is arc-shaped.

[0010] In one embodiment, the second guide plate may also be in a folded line shape.

[0011] In one embodiment, the length a of the first partition extending along the second preset direction and the length b of the first notch along the second preset direction satisfy a>b. It can be understood that such a configuration can ensure that the refrigerant has a sufficient travel length in the cold circulation channel layer, further improving the heat exchange efficiency of the heat exchanger.

[0012] In one embodiment, the first baffle and the bottom wall of the cold circulation channel layer are integrally formed. It can be understood that such a configuration effectively improves the structural strength of the heat exchanger and reduces the difficulty of assembling the first baffle.

[0013] In one of the embodiments, the first partition plate and the bottom wall of the cold circulation channel layer are formed by welding.

[0014] In one embodiment, the deflector plate group and the bottom wall of the thermal circulation channel layer are integrally formed. It can be understood that with such a setting, the structural strength of the heat exchanger is effectively improved, and the assembly difficulty of the deflector plate group is reduced.

[0015] In one embodiment, the deflector plate group and the bottom wall of the thermal circulation channel layer are formed by welding.

[0016] In one embodiment, the distance m between the cold inlet manifold channel and the first partition, and the width n of the first channel along the direction perpendicular to the second preset direction satisfy 1 / 2 < m / n < 1. It can be understood that with such a setting, it is ensured that the distance between the cold inlet manifold channel and the first partition is far enough, thereby further prolonging the flow time of the refrigerant in the cold circulation channel layer.

[0017] In one embodiment, the distance p between the cold outlet manifold channel and the first partition, and the width q of the second channel along the direction perpendicular to the second preset direction satisfy 1 / 2 < p / q < 1. It can be understood that with such a setting, it is ensured that the distance between the cold outlet manifold channel and the first partition is far enough, thereby further prolonging the flow time of the refrigerant in the cold circulation channel layer.

[0018] In one embodiment, fins are provided in the thermal circulation channel layer.

[0019] In one embodiment, fins are provided in the cold circulation channel layer.

[0020] In one embodiment, the heat exchanger includes a plurality of plates and a plurality of heat exchange bumps. Adjacent plates enclose to form a thermal circulation channel layer or a cold circulation channel layer, and one end of each of the plurality of heat exchange bumps is connected to a plate, and the other end abuts against an adjacent plate.

[0021] In one embodiment, the heat exchanger includes a plurality of plates and a plurality of heat exchange ribs. Adjacent plates enclose to form a thermal circulation channel layer or a cold circulation channel layer, and one end of each of the plurality of heat exchange ribs is connected to a plate, and the other end abuts against an adjacent plate.

[0022] Compared with the prior art, for the heat exchanger provided in the present application, the first channel, the first notch and the second channel form a flow path similar to a U shape. Compared with the refrigerant flowing directly from the first end to the second end, in this way, the travel distance of the refrigerant in the cold circulation channel layer is greatly increased, that is, the flow time of the refrigerant in the cold circulation channel layer is greatly increased. When the flow time of the refrigerant in the cold circulation channel layer is prolonged, the contact time between the coolant and the refrigerant is also greatly prolonged, thereby effectively increasing the heat exchange amount between the coolant and the refrigerant.

[0023] In addition, by setting the first partition, the cold circulation channel layer is divided into a first channel and a second channel, which greatly reduces the flow width of the refrigerant in the cold circulation channel layer. The narrower the flow width, the better the flow uniformity of the refrigerant in the cold circulation channel layer. In this way, the refrigerant flows more evenly in the cold circulation channel layer, thereby avoiding the phenomenon of uneven heat exchange of the refrigerant.

[0024] Furthermore, since a guide plate group extending perpendicular to the first preset direction is provided between the first end and the second end of the heat circulation channel layer, and the guide plate group is provided with a plurality of guide channels, the coolant can enter the heat outlet collection channel from the heat inlet collection channel through the plurality of guide channels. In this way, in the process of the coolant entering the second end from the first end, under the guidance of the guide plate group, it can enter different guide channels, and the plurality of guide channels are distributed perpendicular to the first preset direction. Therefore, compared with the coolant directly entering the second end from the first end, the circulation range of the coolant along the first preset direction is greatly improved, thereby increasing the circulation area of ​​the coolant in the heat circulation channel layer, and further improving the heat exchange efficiency of the coolant. In addition, the provision of a plurality of guide channels effectively increases the passing rate of the coolant in the heat circulation channel layer, thereby reducing the resistance encountered by the coolant when circulating in the heat circulation channel layer, and further reducing the power consumption loss of the entire thermal management system.

[0025] Furthermore, because the cold outlet collecting channel is arranged on the side of the third end close to the first end, it can be seen that the settings of the hot inlet collecting channel and the cold outlet collecting channel are relatively close, that is, the outlet of the refrigerant in the cold circulation channel layer is close to the inlet of the coolant in the hot circulation channel layer. In this way, the coolant that has just entered the hot circulation channel layer can reheat the refrigerant that is about to leave the cold circulation channel layer, so that the liquid in the refrigerant is completely vaporized, and it can even ensure that the refrigerant has a certain degree of superheat to avoid liquid hammer after the refrigerant enters the compressor.

[0026] It is understandable that "the cold inlet collecting channel is arranged on the side of the third end close to the second end" means that the heat outlet collecting channel is arranged at a position close to the first channel. It should be noted that in the process of the refrigerant entering the first channel, the first notch and the second channel from the cold inlet collecting channel, the refrigerant absorbs heat through phase change, that is, the refrigerant absorbs heat in the process of changing from liquid to gas, and in the process of the refrigerant phase change and heat absorption, the temperature of the refrigerant hardly changes. Only when the refrigerant completely changes from liquid to gas, the refrigerant continues to absorb heat, which will cause the temperature of the refrigerant to rise. In addition, it can be known from experiments that the refrigerant has not been completely vaporized in the first channel, so the temperature of the refrigerant will hardly rise in the first channel. Therefore, "the cold inlet collecting channel is arranged on the side of the third end close to the second end" can ensure that the coolant will not be heated again by the refrigerant with rising temperature when leaving the cold circulation channel layer, thereby effectively ensuring that the temperature drop of the coolant will not decrease.

[0027] In summary, such a setting not only greatly improves the heat exchange efficiency of the heat exchanger, but also avoids liquid hammer after the refrigerant enters the compressor, thereby greatly improving the service life of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the conventional technology, the drawings required for use in the embodiments or the conventional technology descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0029] Figure 1 A schematic structural diagram of a heat exchanger according to an embodiment of the present application;

[0030] Figure 2 An exploded view of a heat exchanger according to an embodiment of the present application;

[0031] Figure 3 A schematic diagram of the structure of a cold circulation channel layer according to an embodiment of the present application;

[0032] Figure 4 A schematic diagram of the structure of a thermal cycle channel layer according to an embodiment of the present application;

[0033] Figure 5 A schematic diagram of the structure of a thermal cycle channel layer according to another embodiment of the present application;

[0034] Figure 6 A schematic structural diagram of a thermal cycle channel layer according to another embodiment of the present application.

[0035] Figure numerals: 100, hot inlet collecting channel; 110, hot cycle channel layer; 111, first end; 112, second end; 120, hot outlet collecting channel; 130, cold inlet collecting channel; 140, cold cycle channel layer; 141, third end; 142, fourth end; 143, first channel; 144, second channel; 150, cold outlet collecting channel; 200, first partition; 210, first notch; 300, guide plate group; 310, guide channel; 320, second partition; 330, first guide vane; 340, second guide vane; 341, first guide section; 342, second guide section; 400, fin; 500, plate; 600, heat exchange bump. DETAILED DESCRIPTION

[0036] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0037] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0038] In this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0039] In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being “above”, “above”, and “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being “below”, “below”, and “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0040] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and are not intended to be the only implementation method.

[0041] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art to which this application belongs. The terms used herein in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and / or" used herein includes any and all combinations of one or more of the related listed items.

[0042] Usually, in a heat exchanger, the channels where the coolant is located and the channels where the refrigerant is located are cross-layered, and in order to facilitate the installation of pipelines and to increase the heat exchange area of ​​the heat exchanger, the coolant inlet, coolant outlet, refrigerant inlet and refrigerant outlet are respectively located at the four corners of the heat exchanger. However, with such an arrangement, after the heat exchanger completes a heat exchange, the coolant temperature does not drop much, so the heat exchange efficiency of the existing heat exchanger is not high.

[0043] See also Figure 1-Figure 6 In order to improve the heat exchange efficiency of the heat exchanger, the present application provides a heat exchanger, which is provided with a heat inlet collecting channel 100, a multi-layer hot cycle channel layer 110 and a heat outlet collecting channel 120 connected in sequence, and the heat exchanger is also provided with a cold inlet collecting channel 130, a multi-layer cold cycle channel layer 140 and a cold outlet collecting channel 150 connected in sequence. The hot cycle channel layer 110 and the cold cycle channel layer 140 are cross-stacked so that heat can be transferred between adjacent hot cycle channel layers 110 and cold cycle channel layers 140.

[0044] Furthermore, the heat circulation channel layer 110 includes a first end 111 and a second end 112 distributed along a first preset direction, the heat inlet collecting channel 100 is arranged at the first end 111 of the heat circulation channel layer 110, and the heat outlet collecting channel 120 is arranged at the second end 112 of the heat circulation channel layer 110, and a guide plate group 300 extending along a direction perpendicular to the first preset direction is provided between the first end 111 and the second end 112 of the heat circulation channel layer 110, and the guide plate group 300 is provided with a plurality of guide channels 310 distributed along a direction perpendicular to the first preset direction, so that the coolant can enter the heat outlet collecting channel 120 from the heat inlet collecting channel 100 through the plurality of guide channels 310.

[0045] The cold circulation channel layer 140 includes a third end 141 and a fourth end 142 distributed along a second preset direction. The cold inlet collecting channel 130 and the cold outlet collecting channel 150 are both arranged at the third end 141 of the cold circulation channel layer 140. A first partition 200 extending along the second preset direction is provided between the cold inlet collecting channel 130 and the cold outlet collecting channel 150 to divide the cold circulation channel layer 140 into a first channel 143 and a second channel 144, and a first notch 210 is provided at one end of the first partition 200 close to the fourth end 142. The refrigerant can enter the cold outlet collecting channel 150 from the cold inlet collecting channel 130 through the first channel 143, the first notch 210 and the second channel 144 in sequence.

[0046] The cold inlet collecting channel 130 is disposed on a side of the third end 141 close to the second end 112 , and the cold outlet collecting channel 150 is disposed on a side of the third end 141 close to the first end 111 .

[0047] The first channel 143, the first notch 210 and the second channel 144 form a U-shaped flow path, which greatly increases the distance of the refrigerant in the cold circulation channel layer 140, that is, greatly increases the circulation time of the refrigerant in the cold circulation channel layer 140, relative to the refrigerant directly flowing from the first end 111 to the second end 112. When the circulation time of the refrigerant in the cold circulation channel layer 140 is prolonged, the contact time between the coolant and the refrigerant is also greatly prolonged, thereby effectively improving the heat exchange between the coolant and the refrigerant.

[0048] Furthermore, by providing the first partition 200, the cold circulation channel layer 140 is divided into a first channel 143 and a second channel 144, which greatly reduces the flow width of the refrigerant in the cold circulation channel layer 140. The narrower the flow width, the better the flow uniformity of the refrigerant in the cold circulation channel layer 140. In this way, the refrigerant flows more evenly in the cold circulation channel layer 140, thereby avoiding the phenomenon of uneven heat exchange of the refrigerant.

[0049] Furthermore, since a guide plate group 300 extending perpendicularly to the first preset direction is provided between the first end 111 and the second end 112 of the heat circulation channel layer 110, and the guide plate group 300 is provided with a plurality of guide channels 310, the coolant can enter the heat outlet collector channel 120 from the heat inlet collector channel 100 through the plurality of guide channels 310. In this way, in the process of the coolant entering the second end 112 from the first end 111, under the guidance of the guide plate group 300, the coolant can enter different guide channels 310, and the plurality of guide channels 310 are distributed perpendicularly to the first preset direction. Therefore, compared with the coolant directly entering the second end 112 from the first end 111, the circulation range of the coolant along the first preset direction is greatly improved, thereby increasing the circulation area of ​​the coolant in the heat circulation channel layer 110, and further increasing the heat exchange efficiency of the coolant. Furthermore, the provision of a plurality of guide channels 310 effectively increases the flow rate of the coolant in the heat circulation channel layer 110, thereby reducing the resistance encountered by the coolant when circulating in the heat circulation channel layer 110, thereby reducing the power consumption loss of the entire thermal management system.

[0050] Because the cold outlet collecting channel 150 is arranged on the side of the third end 141 close to the first end 111, it can be known that the hot inlet collecting channel 100 and the cold outlet collecting channel 150 are arranged relatively close, that is, the outlet of the refrigerant in the cold circulation channel layer 140 is close to the inlet of the coolant in the hot circulation channel layer 110. In this way, the coolant that has just entered the hot circulation channel layer 110 can reheat the refrigerant that is about to leave the cold circulation channel layer 140, so that the liquid in the refrigerant is completely vaporized, and it can even ensure that the refrigerant has a certain degree of superheat to avoid liquid hammer after the refrigerant enters the compressor.

[0051] It is understandable that "the cold inlet collecting channel 130 is arranged on the side of the third end 141 close to the second end 112" means that the heat outlet collecting channel 120 is arranged at a position close to the first channel 143. It should be noted that in the process of the refrigerant entering the first channel 143, the first notch 210 and the second channel 144 from the cold inlet collecting channel 130, the refrigerant absorbs heat through phase change, that is, the refrigerant absorbs heat during the process of changing from liquid to gas, and in the process of the refrigerant phase change and heat absorption, the temperature of the refrigerant hardly changes. Only when the refrigerant completely changes from liquid to gas, the refrigerant continues to absorb heat, which will cause the temperature of the refrigerant to rise. In addition, it can be seen from experiments that the refrigerant has not been completely vaporized in the first channel 143, so the temperature of the refrigerant hardly rises in the first channel 143. Therefore, "the cold inlet collecting channel 130 is arranged on the side of the third end 141 close to the second end 112", which can ensure that the coolant will not be heated again by the refrigerant with rising temperature when leaving the cold circulation channel layer 140, thereby effectively ensuring that the temperature drop of the coolant will not decrease.

[0052] In summary, such a setting not only greatly improves the heat exchange efficiency of the heat exchanger, but also avoids liquid hammer after the refrigerant enters the compressor, thereby greatly improving the service life of the compressor.

[0053] It should be noted that the heat exchanger is made of a material with high thermal conductivity. For example, the heat exchanger may be made of metal or other non-metallic materials with high thermal conductivity.

[0054] In one embodiment, the angle between the first preset direction and the second preset direction is 70°-110°. Thus, the first preset direction and the second preset direction are approximately vertically arranged.

[0055] In one embodiment, if Figure 2 As shown, the first preset direction and the second preset direction are perpendicular to each other. Such an arrangement effectively reduces the difficulty of arranging the heat inlet manifold 100, the heat outlet manifold 120, the cold inlet manifold 130 and the cold outlet manifold 150, thereby reducing the difficulty of processing the heat exchanger.

[0056] But not limited to this, in other embodiments, the angle between the first preset direction and the second preset direction can also be 70°, 80°, 100° or 110°, which are not listed here one by one.

[0057] In one embodiment, if Figure 4 As shown, the guide plate group 300 includes a second baffle 320 extending perpendicular to the first preset direction, and two guide channels 310 are respectively provided at both ends of the second baffle 320, and the coolant can enter the heat outlet collecting channel 120 from the heat inlet collecting channel 100 through the two guide channels 310. In this way, the processing difficulty of the guide plate group 300 is effectively reduced, thereby reducing the manufacturing cost of the heat exchanger.

[0058] In another embodiment, if Figure 5 As shown, the guide plate group 300 includes a plurality of first guide plates 330 distributed along a first preset direction, and one end of the first guide plate 330 points to the heat inlet collector channel 100, and the other end is distributed in a divergent manner away from the heat inlet collector channel 100, and adjacent first guide plates 330 are distributed at intervals to form a guide channel 310. In this way, the distribution uniformity of the coolant in the heat circulation channel layer 110 is greatly improved, thereby further improving the heat exchange efficiency of the heat exchanger.

[0059] In yet another embodiment, Figure 6As shown, the guide plate group 300 includes a plurality of second guide plates 340 distributed along a first preset direction, and adjacent second guide plates 340 are spaced apart to form a guide channel 310. The second guide plates 340 include a first guide section 341 and a second guide section 342. One end of the first guide section 341 points to the heat inlet collector channel 100, and the other end is distributed in a divergent manner in a direction away from the heat inlet collector channel 100. One end of the second guide section 342 away from the first guide section 341 points to the heat outlet collector channel 120, and one end of the second guide section 342 close to the first guide section 341 is distributed in a divergent manner in a direction away from the heat outlet collector channel 120, and one end of the second guide section 342 away from the first guide section 341 is connected to one end of the first guide section 341 away from the heat inlet collector channel 100. In this way, the uniformity of the distribution of the coolant in the heat circulation channel layer 110 is further improved, thereby further improving the heat exchange efficiency of the heat exchanger.

[0060] Further, in one embodiment, if Figure 6 As shown, the second guide plate 340 is arc-shaped.

[0061] However, the present invention is not limited thereto. In other embodiments, the second guide plate 340 may also be in a folded line shape, that is, the first guide segment 341 and the second guide segment 342 are both in a straight line shape, and the first guide segment 341 and the second guide segment 342 are at an obtuse angle.

[0062] It should be noted that the second guide segment 342 may also be a combination of a straight line and an arc shape.

[0063] In one embodiment, if Figure 3 As shown, the length a of the first partition 200 extending along the second preset direction and the length b of the first notch 210 along the second preset direction satisfy a>b. In this way, it is possible to ensure that the refrigerant has a sufficient travel length in the cold circulation channel layer 140, further improving the heat exchange efficiency of the heat exchanger.

[0064] Furthermore, in one embodiment, 1.2≤a / b≤3. Thus, while ensuring that the refrigerant has a sufficient travel length in the cold circulation channel layer 140 , it also avoids the problem that the length b of the first notch 210 is too small, which makes it difficult for the coolant to enter the second channel 144 from the first channel 143 .

[0065] Furthermore, in one embodiment, the first baffle plate 200 and the bottom wall of the cold circulation channel layer 140 are integrally formed, thereby effectively improving the structural strength of the heat exchanger and reducing the difficulty of assembling the first baffle plate 200 .

[0066] However, it is not limited thereto. In other embodiments, the first partition plate 200 and the bottom wall of the cold circulation channel layer 140 may also be formed by welding.

[0067] Similarly, in one embodiment, the flow guide plate group 300 and the bottom wall of the heat circulation channel layer 110 are integrally formed. In this way, the structural strength of the heat exchanger is effectively improved, and the assembly difficulty of the flow guide plate group 300 is reduced.

[0068] However, it is not limited to this. In other embodiments, the flow guide plate group 300 and the bottom wall of the heat circulation channel layer 110 can also be formed by welding.

[0069] In one embodiment, as Figure 3 shown, the distance m between the cold inlet manifold channel 130 and the first partition 200, and the width n of the first channel 143 along the direction perpendicular to the second preset direction satisfy 1 / 2 < m / n < 1. In this way, it is ensured that the distance between the cold inlet manifold channel 130 and the first partition 200 is far enough, so as to further extend the flow time of the refrigerant in the cold circulation channel layer 140.

[0070] Similarly, in one embodiment, as Figure 3 shown, the distance p between the cold outlet manifold channel 150 and the first partition 200, and the width q of the second channel 144 along the direction perpendicular to the second preset direction satisfy 1 / 2 < p / q < 1. In this way, it is ensured that the distance between the cold outlet manifold channel 150 and the first partition 200 is far enough, so as to further extend the flow time of the refrigerant in the cold circulation channel layer 140.

[0071] In one embodiment, as Figure 2 shown, fins 400 are provided in the heat circulation channel layer 110, or fins 400 are provided in the cold circulation channel layer 140.

[0072] In another embodiment, as Figure 2 shown, the heat exchanger includes a plurality of plates 500 and a plurality of heat exchange bumps 600. Adjacent plates 500 enclose to form the heat circulation channel layer 110 or the cold circulation channel layer 140, and one end of each of the plurality of heat exchange bumps 600 is connected to the plate 500, and the other end abuts against the adjacent plate 500.

[0073] In still another embodiment, the heat exchanger includes a plurality of plates 500 and a plurality of heat exchange ribs (not shown in the figure). Adjacent plates 500 enclose to form the heat circulation channel layer 110 or the cold circulation channel layer 140, and one end of each of the plurality of heat exchange ribs is connected to the plate 500, and the other end abuts against the adjacent plate 500.

[0074] The technical features of the above-described embodiments can be combined arbitrarily. For the sake of brevity of description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope described in this specification.

[0075] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0076] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the scope of patent protection of the present application shall be subject to the attached claims.

Claims

1. A heat exchanger, characterized in that: A heat inlet collecting channel (100), a plurality of heat cycle channel layers (110), and a heat outlet collecting channel (120) are provided, which are connected in sequence; the heat exchanger is also provided with a cold inlet collecting channel (130), a plurality of cold cycle channel layers (140), and a cold outlet collecting channel (150) which are connected in sequence; the heat cycle channel layers (110) and the cold cycle channel layers (140) are cross-layered so that heat can be transferred between adjacent heat cycle channel layers (110) and cold cycle channel layers (140); The heat circulation channel layer (110) comprises a first end (111) and a second end (112) distributed along a first preset direction, the heat inlet collecting channel (100) is arranged at the first end (111) of the heat circulation channel layer (110), the heat outlet collecting channel (120) is arranged at the second end (112) of the heat circulation channel layer (110), and a guide plate group (300) extending perpendicular to the first preset direction is arranged between the first end (111) and the second end (112) of the heat circulation channel layer (110), and the guide plate group (300) is provided with a plurality of guide channels (310) distributed perpendicular to the first preset direction, so that coolant can enter the heat outlet collecting channel (120) from the heat inlet collecting channel (100) through the plurality of guide channels (310); The cold circulation channel layer (140) comprises a third end (141) and a fourth end (142) distributed along a second preset direction; the cold inlet collecting channel (130) and the cold outlet collecting channel (150) are both arranged at the third end (141) of the cold circulation channel layer (140); a first partition (200) extending along the second preset direction is arranged between the cold inlet collecting channel (130) and the cold outlet collecting channel (150) to divide the cold circulation channel layer (140) into a first channel (143) and a second channel (144); and a first notch (210) is arranged at one end of the first partition (200) close to the fourth end (142); and refrigerant can enter the cold outlet collecting channel (150) from the cold inlet collecting channel (130) through the first channel (143), the first notch (210) and the second channel (144) in sequence; The cold inlet collecting channel (130) is arranged on a side of the third end (141) close to the second end (112), and the cold outlet collecting channel (150) is arranged on a side of the third end (141) close to the first end (111); The guide plate group (300) comprises a plurality of first guide plates (330) distributed along a first preset direction, one end of the first guide plate (330) points to the heat inlet collecting channel (100), and the other end is distributed in a divergent manner in a direction away from the heat inlet collecting channel (100), and adjacent first guide plates (330) are distributed at intervals to form the guide channel (310); Alternatively, the guide plate group (300) comprises a plurality of second guide plates (340) distributed along a first preset direction, adjacent second guide plates (340) are spaced apart to form the guide channel (310), the second guide plate (340) comprises a first guide section (341) and a second guide section (342), one end of the first guide section (341) points to the heat inlet collecting channel (100), and the other end is distributed in a divergent manner in a direction away from the heat inlet collecting channel (100), one end of the second guide section (342) away from the first guide section (341) points to the heat outlet collecting channel (120), one end of the second guide section (342) close to the first guide section (341) is distributed in a divergent manner in a direction away from the heat outlet collecting channel (120), and one end of the second guide section (342) away from the first guide section (341) is connected to one end of the first guide section (341) away from the heat inlet collecting channel (100).

2. The heat exchanger according to claim 1, characterized in that: The angle between the first preset direction and the second preset direction is 70°-110°.

3. The heat exchanger according to claim 1, characterized in that: The guide plate group (300) comprises a second baffle (320) extending in a direction perpendicular to a first preset direction, and two guide channels (310) are respectively provided at both ends of the second baffle (320), so that coolant can enter the heat outlet collecting channel (120) from the heat inlet collecting channel (100) through the two guide channels (310).

4. The heat exchanger according to claim 1, characterized in that: The second guide plate (340) is arc-shaped; Alternatively, the second guide plate (340) is in a fold line shape.

5. The heat exchanger according to claim 1, characterized in that: The first partition (200) has a length a extending along the second preset direction, and the first notch (210) has a length b along the second preset direction, satisfying a>b.

6. The heat exchanger according to claim 1, characterized in that The first partition plate (200) and the bottom wall of the cold circulation channel layer (140) are integrally formed; or the first partition plate (200) and the bottom wall of the cold circulation channel layer (140) are welded; And / or, the guide plate group (300) and the bottom wall of the heat circulation channel layer (110) are integrally formed; or, the guide plate group (300) and the bottom wall of the heat circulation channel layer (110) are welded.

7. The heat exchanger according to claim 1, characterized in that The distance m between the cold inlet collecting channel (130) and the first partition (200), and the width n of the first channel (143) along a direction perpendicular to the second preset direction, satisfy, 1 / 2 <m / n<1; And / or, the distance p between the cold outlet collecting channel (150) and the first partition (200), and the width q of the second channel (144) along a direction perpendicular to the second preset direction, satisfy, 1 / 2 <p / q<1。 8. The heat exchanger according to claim 1, characterized in that The heat circulation channel layer (110) is provided with fins (400); And / or, fins (400) are provided in the cold circulation channel layer (140); And / or, the heat exchanger comprises a plurality of plates (500) and a plurality of heat exchange protrusions (600), the adjacent plates (500) are arranged to form the hot cycle channel layer (110) or the cold cycle channel layer (140), and the plurality of heat exchange protrusions (600) are connected to the plates (500) at one end and abutted against adjacent plates (500) at the other end; And / or, the heat exchanger comprises a plurality of plates (500) and a plurality of heat exchange ribs, the adjacent plates (500) are arranged to form the hot cycle channel layer (110) or the cold cycle channel layer (140), and the plurality of heat exchange ribs are connected to the plates (500) at one end and abutted against adjacent plates (500) at the other end.

Images