Plate type collecting pipe and heat exchanger

Abstract

The utility model discloses a plate type collecting pipe and a heat exchanger. The plate type collecting pipe comprises a plurality of plates which are arranged in a stacked mode, the plates comprise end plates, flow plates, flow equalizing plates and flat pipe inserting plates which are sequentially arranged in a stacked mode and jointly define one or more fluid channels, and each fluid channel comprises a flow hole channel and a flat pipe inserting plate, the plurality of flat tube insertion hole channels are formed in the flat tube insertion plate so as to be suitable for insertion of flat tubes; and the flow equalizing hole channel is arranged on the flow equalizing plate and is communicated with the flow path hole channel and the plurality of flat tube insertion hole channels. According to the plate-type collecting pipe, a fluid channel with a small space can be built in the plate-type collecting pipe through the plate-type design, accumulation of refrigerants in the collecting pipe is reduced, the filling amount of the refrigerants is reduced, cost is reduced, and the plate-type collecting pipe is more environmentally friendly. And meanwhile, by introducing the flow equalizing plates and the flow equalizing hole channels, the uniformity of two-phase flow of the refrigerant is improved, and the heat exchanger applying the plate type collecting pipe has high heat exchange efficiency.

Description

Technical Field

[0001] The utility model belongs to the technical field of headers, in particular to a plate-type header and a heat exchanger. Background Art

[0002] The heat exchanger works by the phase change between the gas phase and the liquid phase of the refrigerant fluid, including the condenser and the evaporator. In the condenser, the refrigerant releases heat and changes from the gas phase to the liquid phase, while in the evaporator, the refrigerant absorbs heat and changes from the liquid phase to the gas phase to exchange heat. In this way, in the heat exchanger, the refrigerant is always in the form of a two-phase flow of liquid and gas phases.

[0003] Compared with traditional tube-fin heat exchangers, microchannel heat exchangers have the characteristics of compact structure, high heat exchange efficiency and low cost. In particular, its micro-scale flat tube structure can greatly reduce the internal volume of the heat exchanger, reducing the system refrigerant charge by more than 35%. At present, the US EPA and European HPA have listed microchannel heat exchangers as energy-saving and emission-reduction technologies and key research areas; and the "China Home Appliance Industry Technology Roadmap" also lists microchannel heat exchangers as a key development direction.

[0004] In the prior art, microchannel heat exchangers mostly use a circular tube header solution, where the refrigerant flows from the header into several flat tubes, and the refrigerant undergoes phase change heat transfer during the flow process. Ideally, the two phases of the refrigerant are evenly distributed in the flat tubes, and the overall heat exchange efficiency of the heat exchanger is the best. In addition, the smaller the volume of the header, the more conducive it is to reducing the accumulation of refrigerant in the header. However, due to its structural characteristics, the current circular tube header has a large internal space that causes a large amount of refrigerant accumulation. At the same time, it is difficult to set a flow equalization component inside the circular tube header, which is not conducive to the regulation of the uniformity of the two phases of the refrigerant. Utility Model Content

[0005] In view of the above technical problems, the utility model provides a plate-type header and a heat exchanger including the plate-type header. The plate-type header can effectively reduce the accumulation of refrigerant in the header, reduce the refrigerant charge in the heat exchanger, and improve the uniformity of the refrigerant two-phase flow.

[0006] To this end, according to one aspect of the concept of the utility model, a plate-type collector is proposed, which includes a plurality of plates arranged in a stacked manner, and the plurality of plates include end plates, flow plates, flow balancing plates and flat tube insertion plates which are stacked in sequence, and jointly define one or more fluid channels, and the fluid channels include: a flow channel, which is arranged on the flow plate; a plurality of flat tube insertion channels, which are arranged on the flat tube insertion plate to be suitable for flat tube insertion; and a flow balancing channel, which is arranged on the flow balancing plate and is connected to the flow channel and the plurality of flat tube insertion channels.

[0007] According to the above technical concept, the utility model may further include any one or more of the following optional forms.

[0008] According to some optional forms, at least one of the fluid channels is configured as an inlet and outlet fluid channel, and the inlet and outlet fluid channel includes at least one fluid hole for fluid inflow or outflow, and the fluid hole is arranged on the end plate. In the inlet and outlet fluid channel, the fluid hole is connected to the flow channel.

[0009] According to some optional forms, the number of the inlet and outlet fluid channels is two or more, and each of the inlet and outlet fluid channels includes the fluid hole for fluid to flow in or out.

[0010] According to some optional forms, at least one of the fluid channels is configured as a return fluid channel, and the return fluid channel is suitable for being connected to the inlet and outlet fluid channels.

[0011] According to some optional forms, the flow balancing plate includes a first flow balancing plate, which is stacked between the process plate and the flat tube insertion plate, and the flow balancing channel includes: a plurality of first flow balancing channels, which are arranged on the first flow balancing plate and connected to the process channel and the plurality of flat tube insertion channels, forming a partition area between two adjacent first flow balancing channels.

[0012] According to some optional forms, in the inlet and outlet fluid channels, the fluid holes are aligned with the partition areas.

[0013] According to some optional forms, a first groove is provided on the first flow balancing plate, and the first groove runs through the partition area to connect the first flow balancing channels.

[0014] According to some optional forms, the flow balancing plate also includes a second flow balancing plate, which is stacked between the first flow balancing plate and the flat tube insertion plate, and the flow balancing channel also includes: a plurality of second flow balancing channels, which are arranged on the second flow balancing plate and connected to the plurality of first flow balancing channels and the plurality of flat tube insertion channels, and a second groove is arranged on the second flow balancing plate to connect the second flow balancing channels.

[0015] According to some optional forms, the multiple plates also include a flat tube positioning plate, which is stacked between the flow equalizing plate and the flat tube insertion plate and is suitable for abutting against the end of the flat tube inserted in the flat tube insertion channel, and the fluid channel includes a flat tube positioning channel, which is arranged on the flat tube positioning plate and is connected to the flow equalizing channel and the flat tube insertion channel.

[0016] According to some optional forms, the size of the flat tube positioning channel is smaller than the size of the flat tube insertion channel.

[0017] According to some optional forms, the thickness of each of the plates is 0.3 mm to 3 mm.

[0018] According to some optional forms, each of the plates is made of metal and is laminated together by brazing.

[0019] According to another aspect of the present invention, a heat exchanger is provided, comprising flat tubes. The heat exchanger further comprises the plate-type header, wherein the flat tubes are inserted into the flat tube insertion holes of the plate-type header.

[0020] The plate-type header of the utility model can construct a fluid channel with a small space inside it through the plate-type design, reduce the accumulation of refrigerant in the header, reduce the amount of refrigerant charged, reduce costs and be more environmentally friendly. At the same time, by introducing the flow equalizing plate and the flow equalizing channel, the uniformity of the refrigerant two-phase flow is improved, so that the heat exchanger using the plate-type header has a higher heat exchange efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The features, advantages and other aspects of the various embodiments of the present invention will become more apparent with reference to the following detailed description in conjunction with the accompanying drawings. Several embodiments of the present invention are shown herein in an illustrative and non-restrictive manner. In the accompanying drawings, the same figure marks represent the same or similar parts.

[0022] Figure 1 is a schematic diagram of an exemplary plate-type header according to the utility model;

[0023] Figure 2 yes Figure 1 An exploded view of the plate-type header shown;

[0024] Figure 3 is an exploded view of an exemplary plate-type header according to the utility model;

[0025] Figure 4 is a schematic diagram of another exemplary plate-type header according to the utility model;

[0026] Figure 5 yes Figure 4 An exploded view of the plate-type header shown;

[0027] Figure 6 is an exploded view of another exemplary plate-type header according to the utility model;

[0028] Figure 7 and Figure 8 1 is an exploded view of two other exemplary plate-type headers according to the present invention;

[0029] Fig. 9 is a schematic diagram of an exemplary heat exchanger according to the present invention;

[0030] Figures 10 to 15 The refrigerant flow path of an exemplary heat exchanger according to the present invention is illustrated.

[0031] Figure markings: 10-end plate; 11-fluid hole; 20-flow plate; 21-flow channel; 30-flat tube insertion plate; 31-flat tube insertion channel; 40-first flow equalizing plate; 41-first flow equalizing channel; 42-partitioning area; 43-first groove; 50-second flow equalizing plate; 51-second flow equalizing channel; 52-second groove; 60-flat tube positioning plate; 61-flat tube positioning channel; 71-flat tube; 72-fin; I-plate-type header; II-heat exchanger; III-another opposite header; C-fluid channel; C1-inlet and outlet fluid channel; C2-return fluid channel. DETAILED DESCRIPTION

[0032] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0033] It should be noted that if a directional indication is involved in the embodiments of the present invention, the directional indication is only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0034] In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the fact that ordinary technicians in the field can implement it. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by the present utility model.

[0035] In view of the fact that in the prior art, heat exchangers conventionally use cylindrical headers, there are problems such as large refrigerant accumulation and high refrigerant consumption, and it is difficult to uniformly regulate the two phases of the refrigerant, which makes the gas phase and liquid phase in the refrigerant uneven, affecting the heat exchange effect. The utility model proposes a plate-type header. The heat exchanger using the plate-type header has the advantages of less refrigerant consumption, and the two-phase flow of the refrigerant is uniform, and the overall heat exchange efficiency is high.

[0036] Figure 1 and Figure 2An exemplary embodiment of a plate-type manifold I according to the utility model is shown. The plate-type manifold I includes a plurality of plates arranged in a stacked manner, and the plurality of plates include an end plate 10, a process plate 20, a flow equalizing plate, and a flat tube insertion plate 30 arranged in a stacked manner in sequence, and defines a fluid channel C, in which the refrigerant flows. A fluid channel C correspondingly includes a process channel 21 arranged on the process plate 20, a flow equalizing channel arranged on the flow equalizing plate, and a plurality of flat tube insertion channels 31 arranged on the flat tube insertion plate 30, wherein the plurality of flat tube insertion channels 31 can be inserted into the flat tubes, and the flow equalizing channel is connected with the process channel 21 and the plurality of flat tube insertion channels 31. According to actual needs, plates of different thicknesses (especially the process plate 20) can be selected simply and conveniently to make the manifold, for example, the thickness of the process plate 20 can be 0.3 mm to 3 mm, and a process channel 21 of a suitable size can be opened on the process plate 20. In this way, under the premise of ensuring that the refrigerant in the flow channel 21 of the fluid channel C has sufficient accumulation, the plate-shaped flow plate 20 is convenient for making the volume of the flow channel 21 as small as possible, so that the accumulation of refrigerant in the manifold is as small as possible, the overall amount of refrigerant is small, and it has good economy and environmental protection. The number of equal flow channels can be multiple, and the fluid channel C is divided into different flow paths, which can promote the uniformity of the gas phase and liquid phase distribution of the refrigerant and improve the heat exchange efficiency.

[0037] In some embodiments, at least one fluid channel C is configured as an inlet and outlet fluid channel C1, and the inlet and outlet fluid channel C1 includes at least one fluid hole 11, and the fluid hole 11 is arranged on the end plate 10. In the inlet and outlet fluid channel C1, the fluid hole 11 is connected to the flow channel 21 and is used for fluid (such as refrigerant) to flow into or out of the inlet and outlet fluid channel C1.

[0038] It should be understood that the number of fluid channels C and the inlet and outlet fluid channels C1 therein can be set according to actual conditions, and the following is an explanation with reference to the accompanying drawings, in which the unidirectional arrows indicate the fluid / refrigerant flow path (hereinafter referred to as the flow path). Figures 1 to 3 As shown, the number of fluid channels C is one and they are configured as inlet and outlet fluid channels C1, and the fluid holes 11 thereon allow the refrigerant to flow in. The refrigerant is charged into the inlet and outlet fluid channels C1 from the fluid holes 11, first enters the process channel 21, and then is divided from the process channel 21 to the equal flow channel and multiple flat tube insertion channels 31 before entering the flat tubes. Fig.10 In the heat exchanger II shown in FIG. 1 , the refrigerant flows out of the heat exchanger II from the other opposite header III. Figure 4 and Figure 5 As shown, there are two fluid channels C and both are configured as inlet and outlet fluid channels C1, one of which is used for refrigerant inflow and the other is used for refrigerant outflow. Fig.11In the heat exchanger II shown, Fig.11 In the heat exchanger II shown, the refrigerant flows into the heat exchanger II from a fluid hole 11 of the header I, flows into the other opposite header III through the flat tubes, flows back to the header I through the flat tubes, and finally flows out of the heat exchanger II from another fluid hole 11 of the header I. Figure 6 In the embodiment shown, the number of fluid channels C is three and two of them are configured as inlet and outlet fluid channels C1. Among the two inlet and outlet fluid channels C1, one inlet and outlet fluid channel C1 and the fluid hole 11 thereon can be used for refrigerant inflow, the other inlet and outlet fluid channel C1 and the fluid hole 11 thereon can be used for refrigerant outflow, and the third fluid channel C is configured as a return fluid channel C2. The return fluid channel C2 can be connected to the above two inlet and outlet fluid channels C1. For example, when used in a heat exchanger, the return fluid channel C2 can be connected to the above two inlet and outlet fluid channels C1 through a flat tube and another opposite manifold III, as shown in FIG. Fig.12 Heat exchanger II shown. Fig.12 The heat exchanger II shown includes a plate-type header I and another opposite header III. The plate-type header I is connected to the other opposite header III through a flat tube. The refrigerant flows into the heat exchanger II from a fluid hole 11 of the header I, flows into the other opposite header III through the flat tube, then flows back to the header I through the flat tube, and flows into the other opposite header III through the reflux fluid channel C2 of the header I through the flat tube again, then flows back to the header I through the flat tube and flows out of the heat exchanger II from the other fluid hole 11 of the header I.

[0039] It should be understood that the other current collector III is not particularly limited, and can be a plate-type current collector I in an appropriate form, or other suitable current collectors. It should also be understood that the positions of the different fluid channels C in the plate-type current collector I are not particularly limited, and the different fluid channels C can be as follows: Figure 1 and Figure 6 The fins can be arranged vertically up and down as shown, or horizontally side by side (not shown), etc., as needed. This also makes the arrangement of flat tubes and fins more flexible in the heat exchanger using the plate-type header according to the utility model.

[0040] It should be understood that the above is only an exemplary description of the use of the fluid channel C, the inlet and outlet fluid channel C1, and the return fluid channel C2 in the plate-type header, and does not constitute a limitation. There are many other ways of use. For example, when the number of the inlet and outlet fluid channels C1 is two or more, all the inlet and outlet fluid channels C1 and the fluid holes 11 thereon can be used for the inflow or outflow of fluid (such as refrigerant), for example Fig.14In the heat exchanger II shown, the inlet and outlet fluid channels C1 of the plate-type header I have two fluid holes 11, both of which are used for the refrigerant to flow into the heat exchanger II. Afterwards, the refrigerant flows into the other opposite header III through the flat tubes and flows out of the heat exchanger II from the header III. The dotted line and arrows indicate the flow path of the refrigerant in the heat exchanger II. For another example, the number of fluid channels C on the header I can be two, one of which is configured as the inlet and outlet fluid channel C1, and the other is configured as the return fluid channel C2. When used in a heat exchanger, Fig.13 As shown, the heat exchanger II includes a plate-type header I and another opposite header III, and the return fluid channel C2 can be connected to the inlet and outlet fluid channel C1 through the flat tube and the opposite another header III. The fluid / refrigerant flows into the heat exchanger II from a fluid hole 11 of the header I, flows into the opposite another header III through the flat tube, and then flows back to the header I through the flat tube, and flows into the opposite another header III through the return fluid channel C2 of the header I through the flat tube again and flows out of the heat exchanger II from the opposite another header III, wherein the dotted line and arrow indicate the flow path of the refrigerant in the heat exchanger II.

[0041] It should be understood that, according to actual use, for example, in a heat exchanger, the number of inlet and outlet fluid channels C1 of the plate-type manifold I can be two or more, and a single inlet and outlet fluid channel C1 can have one or more fluid holes 11, and the fluid holes 11 on a single inlet and outlet fluid channel C1 can all be used for fluid inflow or fluid outflow. The fluid holes 11 of each inlet and outlet fluid channel C1 can be used for fluid inflow or outflow. Fig.15 In the heat exchanger II shown, the plate-type header I has two inlet and outlet fluid channels C1, which are used for refrigerant inflow and outflow respectively. At the same time, each inlet and outlet fluid channel C1 has two fluid holes 11. The refrigerant flows into the heat exchanger II from the two fluid holes 11 of one of the inlet and outlet fluid channels C1, flows into the other opposite header III through the flat tube, flows back to the header I through the flat tube, and flows out of the heat exchanger II from the two fluid holes 11 of the other inlet and outlet fluid channel C1 of the header I, wherein the dotted line and arrow indicate the flow path of the refrigerant in the heat exchanger II. This is also one of the ways to use the plate-type header I, and is not particularly limited.

[0042] It should be understood that the fluid channel C can be configured as an inlet and outlet fluid channel C1 and a return fluid channel C2, that is, the inlet and outlet fluid channel C1 and the return fluid channel C2 themselves are a kind of fluid channel C, so that the characteristics and limitations of the fluid channel C naturally apply to the inlet and outlet fluid channel C1 and the return fluid channel C2, while the characteristics and limitations of the inlet and outlet fluid channel C1 and the return fluid channel C2 only apply to the inlet and outlet fluid channel C1 and the return fluid channel C2 themselves.

[0043] In some embodiments, Figure 2 As shown, the flow equalizing plates of the multiple plates of the plate-type manifold I include a first flow equalizing plate 40, which is stacked between the process plate 20 and the flat tube insertion plate 30. The flow equalizing channel includes a plurality of first flow equalizing channels 41, which are arranged on the first flow equalizing plate 40, and the process channel 21 and the plurality of flat tube insertion channels 31 are connected between the process channel 21 and the plurality of flat tube insertion channels 31. The shapes and sizes of different first flow equalizing channels 41 can be designed as needed to divide the fluid channel C into different flow paths, and each first flow equalizing channel 41 corresponds to a flow path, thereby playing a role in flow equalization. Figure 7 and Figure 8 The figure shows some situations of first flow equalizing channels 41 of different shapes and sizes. At the same time, a partition 42 is formed between adjacent first flow equalizing channels 41, and each first flow equalizing channel 41 on the first flow equalizing plate 40 is separated from each other by the partition 42. Moreover, in the inlet fluid channel C1, the fluid hole 11 can be aligned with one of the partitions 42. When the inlet and outlet fluid channels C1 and the fluid holes 11 thereon are used for charging the refrigerant into the manifold I, the refrigerant charged from the fluid hole 11 passes through the flow channel 21 and hits the partition 42 aligned with the fluid hole 11, fills the flow channel 21 after scattering, and then enters the flat tube insertion channel 31 after passing through the first flow equalizing channel 41, and the kinetic energy of the refrigerant when charged is used to mix the refrigerant to ensure the uniformity of the two-phase flow. When the inlet and outlet fluid channel C1 and the fluid hole 11 thereon are used for the refrigerant to flow out of the collecting pipe I, the fluid hole 11 can be aligned with one of the partition areas 42, and the refrigerant needs to bypass the partition area 42 aligned with the fluid hole 11 and then flow out from the fluid hole 11. The partition area 42 forms an obstacle to the outflow of the refrigerant to a certain extent, avoiding the sudden decrease in the refrigerant flow pressure near the fluid hole 11 and the subsequent unstable refrigerant flow in the flat tube, thereby maintaining the uniformity of the refrigerant two-phase flow.

[0044] In certain embodiments, such as Figure 3As shown, a first groove 43 is provided on the first flow equalizing plate 40. The first groove 43 can be provided on at least one or all of the partitions 42. The first groove 43 penetrates the partitions 42 and connects the first flow equalizing holes 41 between the first flow equalizing holes 41, so that the refrigerant can flow along the flow path in the fluid channel C and also partially flow in a direction perpendicular to the flow path (as shown by the double-headed arrows in the attached figure), so as to equalize the two phases of the refrigerant, which is particularly suitable for the case where the refrigerant flow rate is large. Taking the inlet and outlet fluid channel C1 for the inflow of the refrigerant as an example, after the two-phase flow of the refrigerant enters the flow channel 21 from the fluid hole 11, since the density of the liquid phase is greater than that of the gas phase, the liquid phase has a greater inertia, so that more liquid phases quickly rush to the area of ​​the flow channel 21 away from the fluid hole 11, while the gas phase has a smaller inertia and is more distributed in the area close to the fluid hole 11, resulting in uneven distribution of the two phases. The first groove 43 provides a channel, which is conducive to the refrigerant with a large amount of liquid phase and located in the area away from the fluid hole 11 to flow toward the area close to the fluid hole 11, which is mainly reflected in: on the one hand, after entering the first equalizing flow channel 41, the liquid phase away from the fluid hole 11 inertia impacts the area away from the fluid hole 11 and then rebounds toward the fluid hole 11. In this way, through the first groove 43 between adjacent first equalizing flow channels 41, the liquid phase can flow from the first equalizing flow channel 41 away from the fluid hole 11 to the first equalizing flow channel 41 close to the fluid hole 11, so that the distribution of the gas-liquid two-phase refrigerant is uniform. On the other hand, after the refrigerant is charged, the refrigerant in the area far away from the fluid hole 11 loses more kinetic energy, and the flow rate is slower than the refrigerant in the area close to the fluid hole 11. According to Bernoulli's principle, the pressure in the area with low flow rate is high, and the pressure in the area with high flow rate is low. Therefore, under the action of the pressure difference, the refrigerant partially flows through the first groove 43 from the first flow equalizing channel 41 far away from the fluid hole 11 to the first flow equalizing channel 41 close to the fluid hole 11, which also makes the distribution of the gas-liquid two-phase of the refrigerant uniform.

[0045] In some embodiments, Figure 2As shown, the flow equalizing plates of the multiple plates of the plate-type collector I further include a second flow equalizing plate 50, which is stacked between the first flow equalizing plate 40 and the flat tube insertion plate 30. The flow equalizing channel further includes a plurality of second flow equalizing channels 51, which are arranged on the second flow equalizing plate 50, and the plurality of first flow equalizing channels 41 and the plurality of flat tube insertion channels 31 are connected between the plurality of first flow equalizing channels 41 and the plurality of flat tube insertion channels 31. A second groove 52 is arranged on the second flow equalizing plate 51, and the second groove 52 connects the plurality of second flow equalizing channels 51 between the plurality of second flow equalizing channels 51, so that the refrigerant can flow partially in a direction perpendicular to the flow path while flowing along the flow path in the fluid channel C, and the two phases of the refrigerant are homogenized. The second groove 52 can be aligned with the first flow equalizing channel 41 and / or the partition area 42 on the first flow equalizing plate 40, and the setting mode and function of the second groove 52 are roughly the same as the setting mode and function of the first groove 43, which will not be repeated here. The difference is that in the inlet and outlet fluid channel C1 for the inflow of refrigerant, after the refrigerant filled in the flow channel 21 hits the partition area 42 and flows through the first flow equalizing plate 40, the refrigerant flow rate entering the second flow equalizing channel 51 is relatively stable and less affected by the refrigerant charging action, which is more conducive to the uniform distribution of the two phases of the refrigerant in the direction perpendicular to the flow path under the action of the above-mentioned pressure difference.

[0046] In some embodiments, Figure 2 As shown, the plurality of plates of the plate-type header 1 further include a flat tube positioning plate 60, which is adjacent to the flat tube insertion plate 30 and is stacked between the flow balancing plate and the flat tube insertion plate 30. After the flat tubes are inserted into the flat tube insertion channels 31, the ends of the flat tubes can abut against the flat tube positioning plate 60, so that the insertion depths of the flat tubes are the same. At the same time, the flat tube positioning plate 60 is provided with a flat tube positioning channel 61, which, as a part of the fluid channel C, is connected to the flat tube insertion channel 31 and the flow balancing channel. It should be understood that, as required, the number of the flow equalizing plates is one or more, and the flow equalizing plates may include the first flow equalizing plate 40 or the first flow equalizing plate 40 and the second flow equalizing plate 50. Thus, in different embodiments, the first flow equalizing plate 40 or the first flow equalizing plate 40 and the second flow equalizing plate 50 may be selectively arranged between the flat tube positioning plate 60 and the process plate 20, and the flat tube positioning channel 61 may be connected to the process channel 21 via the first flow equalizing channel 41 or the first flow equalizing channel 41 and the second flow equalizing channel 51. In terms of design, the size of the flat tube positioning channel 61 may be slightly smaller than the size of the flat tube insertion channel 31, so that the flat tube can be inserted into the flat tube insertion channel 31 and then abut against the flat tube positioning plate 60.

[0047] It should be understood that, according to a specific embodiment, the plate-type current collector I includes a plurality of plates which may correspond to the end plate 10, the flow plate 20, the flat tube insertion plate 30, the first flow balancing plate 40, the second flow balancing plate 50 and the flat tube positioning plate 60, respectively, and the thickness of each plate may be selected as 0.3 mm to 3 mm as required. At the same time, the number of the end plate 10, the flow plate 20, the flat tube insertion plate 30, the first flow balancing plate 40, the second flow balancing plate 50 and the flat tube positioning plate 60 of the plate-type current collector I can be set as required, for example, the plate-type current collector I may have one or more stacked flow plates 20, one or more stacked first flow balancing plates 40, one or more stacked second flow balancing plates 50, and so on. For example, the number of flow balancing plates (which may include the first flow balancing plate 40 and the second flow balancing plate 50) may be one or more, such as Figure 7 As shown, the flow balancing plate of the plate-type current collector 1 includes / is configured as two first flow balancing plates 40, and the two first flow balancing plates 40 are configured with different first flow balancing channels 41 to achieve flow balancing; Figure 8 As shown, the flow equalizing plate of the plate-type collector 1 includes / is configured as two first flow equalizing plates 40 and one second flow equalizing plate 50, and the two first flow equalizing plates 40 are configured with different first flow equalizing channels 41 to achieve flow equalization, and then further flow equalization is achieved through the second flow equalizing channels 51 and the second grooves 52 on the second flow equalizing plate 50. In addition, the above-mentioned plates (which may include the end plate 10, the process plate 20, the flat tube insertion plate 30, the first flow equalizing plate 40, the second flow equalizing plate 50 and the flat tube positioning plate 60) can be made of metal (preferably aluminum alloy) and stacked into one by brazing, so as to well prevent refrigerant leakage.

[0048] Fig. 9 An exemplary heat exchanger II according to the utility model is shown in an exemplary manner. The heat exchanger II includes flat tubes 71, fins 72 and a plate-type collecting pipe I. The flat tubes 71 are inserted into the flat tube insertion channels 31. The flat tubes 71 are flow channels for the refrigerant. The fins 72 connected between the flat tubes 71 are used for heat exchange between the refrigerant and the outside through heat conduction. Figures 10 to 12 The use of Figure 2 , Figure 5 and Figure 6 The heat exchanger II of the plate-type header I is shown, wherein the dotted line and arrows indicate the flow path of the refrigerant in the heat exchanger II.

[0049] It should be understood that the above description of the preferred embodiment is relatively detailed and cannot be regarded as limiting the scope of patent protection of the utility model. Under the enlightenment of the utility model, ordinary technicians in this field can also make substitutions or modifications without departing from the scope of protection of the claims of the utility model, which all fall within the scope of protection of the utility model. The scope of protection requested for the utility model shall be based on the attached claims.

Claims

1. A plate-type header, characterized in that: The plate-type header comprises a plurality of plates arranged in a stacked manner, wherein the plurality of plates comprises an end plate (10), a flow plate (20), a flow balancing plate and a flat tube insertion plate (30) which are sequentially stacked and define one or more fluid channels (C) together, wherein the fluid channels (C) comprise: A process channel (21), wherein the process channel (21) is arranged on the process plate (20); A plurality of flat tube insertion holes (31), wherein the plurality of flat tube insertion holes (31) are arranged on the flat tube insertion plate (30) to be suitable for inserting the flat tubes; A flow balancing channel, wherein the flow balancing channel is arranged on the flow balancing plate and is connected to the flow channel (21) and the plurality of flat tube insertion channels (31).

2. The plate-type header according to claim 1, characterized in that: At least one of the fluid channels (C) is configured as an inlet and outlet fluid channel (C1), and the inlet and outlet fluid channel (C1) includes at least one fluid hole (11) for fluid inflow or outflow, and the fluid hole (11) is arranged on the end plate (10). In the inlet and outlet fluid channel (C1), the fluid hole (11) is connected to the flow channel (21).

3. The plate-type header according to claim 2, characterized in that: The number of the inlet and outlet fluid channels (C1) is two or more, and each of the inlet and outlet fluid channels (C1) comprises the fluid hole (11) for fluid to flow in or out.

4. The plate-type header according to claim 2, characterized in that: At least one of the fluid channels (C) is configured as a return fluid channel (C2), and the return fluid channel (C2) is suitable for being connected to the inlet and outlet fluid channel (C1).

5. The plate-type header according to claim 2, characterized in that: The flow balancing plate comprises a first flow balancing plate (40), wherein the first flow balancing plate (40) is stacked between the process plate (20) and the flat tube insertion plate (30), and the flow balancing channel comprises: A plurality of first flow balancing channels (41), wherein the plurality of first flow balancing channels (41) are arranged on the first flow balancing plate (40) and are connected to the flow channel (21) and the plurality of flat tube insertion channels (31), and a separation area (42) is formed between two adjacent first flow balancing channels (41).

6. The plate-type header according to claim 5, characterized in that: In the inlet and outlet fluid channel (C1), the fluid hole (11) is aligned with the partition area (42).

7. The plate-type header according to claim 5, characterized in that: A first groove (43) is provided on the first flow balancing plate (40), and the first groove (43) penetrates the partition area (42) to connect the first flow balancing channel (41).

8. The plate-type header according to claim 5, characterized in that: The flow balancing plate further comprises a second flow balancing plate (50), wherein the second flow balancing plate (50) is stacked between the first flow balancing plate (40) and the flat tube insertion plate (30), and the flow balancing channel further comprises: A plurality of second flow balancing channels (51), wherein the plurality of second flow balancing channels (51) are arranged on the second flow balancing plate (50) and are connected to the plurality of first flow balancing channels (41) and the plurality of flat tube insertion channels (31), and a second groove (52) is arranged on the second flow balancing plate (50) to connect the second flow balancing channels (51).

9. The plate-type header according to any one of claims 1 to 8, characterized in that: The plurality of plates further include a flat tube positioning plate (60), the flat tube positioning plate (60) being stacked between the flow balancing plate and the flat tube insertion plate (30) and being adapted to abut against the end of the flat tube inserted into the flat tube insertion channel (31), the fluid channel (C) including a flat tube positioning channel (61), the flat tube positioning channel (61) being arranged on the flat tube positioning plate (60) and being in communication with the flow balancing channel and the flat tube insertion channel (31).

10. The plate-type header according to claim 9, characterized in that: The size of the flat tube positioning channel (61) is smaller than the size of the flat tube insertion channel (31).

11. The plate-type header according to claim 9, characterized in that: The thickness of each of the plates is 0.3 mm to 3 mm.

12. The plate-type header according to claim 9, characterized in that: Each of the plates is made of metal and is laminated into one body by brazing.

13. A heat exchanger, comprising a flat tube (71), characterized in that: The heat exchanger (II) further comprises a plate-type header according to any one of claims 1 to 12, wherein the flat tubes (71) are inserted into the flat tube insertion channels (31) of the plate-type header.

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