CN220472395U - Plate heat exchanger with high-efficient profile of tooth - Google Patents
Plate heat exchanger with high-efficient profile of tooth Download PDFInfo
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- CN220472395U CN220472395U CN202320802873.9U CN202320802873U CN220472395U CN 220472395 U CN220472395 U CN 220472395U CN 202320802873 U CN202320802873 U CN 202320802873U CN 220472395 U CN220472395 U CN 220472395U
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- 239000003507 refrigerant Substances 0.000 claims abstract description 103
- 239000002826 coolant Substances 0.000 claims abstract description 17
- 238000000034 method Methods 0.000 claims description 2
- 239000012530 fluid Substances 0.000 description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 2
- 238000003475 lamination Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Abstract
The utility model relates to the field of plate heat exchangers, in particular to a plate heat exchanger with high-efficiency tooth shapes, which comprises a plurality of first plates and second plates which are alternately stacked, wherein a refrigerant heat exchange cavity and a secondary refrigerant heat exchange cavity are alternately formed between the first plates and the second plates; concave-convex structures are regularly arranged in the heat exchange areas of the first plate and the second plate along the longitudinal direction, and the concave-convex structures comprise ridges and grooves which are arranged at equal heights, and the concave-convex structures along the first plate and the second plate are mutually symmetrical along the joint surfaces of the first plate and the second plate; a refrigerant flow channel is formed between the first plate and the second plate below the first plate, and a secondary refrigerant flow channel is formed between the first plate and the second plate above the first plate; the cross-sectional area of the coolant flow passage is greater than the cross-sectional area of the coolant flow passage. The plate heat exchanger constructs the secondary refrigerant flow channels and the refrigerant flow channels with different sectional areas on the basis of not reducing the strength of the plate, and is used for improving the heat exchange efficiency.
Description
Technical Field
The utility model relates to the field of plate heat exchangers, in particular to a plate heat exchanger with high-efficiency tooth shapes.
Background
In recent years, plate heat exchangers are widely used in the industries such as refrigeration industry, air conditioning industry, heat pump system industry, heat treatment industry, petrochemical industry, energy industry, waste heat recovery industry and the like. The construction and operation principle of the plate heat exchanger is to use metal sheets having a corrugation pattern and stacked together. A plurality of fluid channels are formed between the metal sheets, so that heat exchange can be carried out between two fluids (such as liquid to liquid or liquid to steam) according to the heat transfer characteristic of the metal sheets, and the purpose of heating or cooling is achieved. The plate heat exchanger has the advantages of compact structure, high heat transfer efficiency, small volume, easy maintenance and inspection and the like.
The prior plate heat exchanger can refer to a plate heat exchanger described in Chinese patent publication No. CN2821502Y, and comprises a front outer baffle, a rear outer baffle and a plurality of corrugated plates arranged between the front outer baffle and the rear outer baffle; the front outer baffle plate, the rear outer baffle plate and a plurality of corrugated sheets in the front outer baffle plate and the rear outer baffle plate alternately form a refrigerant heat exchange cavity and a secondary refrigerant heat exchange cavity, and the refrigerant and the secondary refrigerant realize heat exchange on two sides of the corrugated sheets. In practical applications, the fluid of the plate heat exchanger is usually a two-phase mixed fluid, and two-phase flow distribution is critical to the evaporation performance of the plate heat exchanger.
On the basis, the prior art, such as the Chinese patent documents with publication numbers of CN206410590U, CN218723394U and CN114945789A, describes a plate heat exchanger with high-efficiency tooth shape, and the prior art constructs bulges with different heights on the heat exchange plates, so that narrow channels and wide channels are formed when the heat exchange plates are combined, and the heat exchange plates are convenient for passing through media with different temperatures respectively, thereby being beneficial to improving the heat exchange efficiency of the prepared heat exchanger.
However, the strength of the plate heat exchanger is reduced because short bulges on two heat exchange plates are not contacted.
Disclosure of Invention
In order to solve the problems, the utility model aims to provide the plate heat exchanger with the high-efficiency tooth shape, and the plate heat exchanger is used for constructing the secondary refrigerant flow channels and the refrigerant flow channels with different sectional areas on the basis of not reducing the strength of the plate, so that the heat exchange efficiency is improved.
In order to achieve the above purpose, the present utility model adopts the following technical scheme:
a plate heat exchanger with high-efficiency tooth shape comprises a plurality of first plates and second plates which are alternately stacked, wherein a refrigerant heat exchange cavity and a secondary refrigerant heat exchange cavity are alternately formed between the first plates and the second plates; the opposite end angles of the first plate and the second plate are respectively provided with a refrigerating medium inlet and a refrigerating medium outlet, and a refrigerating medium inlet and a refrigerating medium outlet; the refrigerating medium inlet and the refrigerating medium outlet on the first plate sheet and the second plate sheet are correspondingly connected to form a refrigerating medium input channel and a refrigerating medium output channel which are communicated with the refrigerating medium heat exchange cavity, and the refrigerating medium inlet and the refrigerating medium outlet are correspondingly connected to form a refrigerating medium input channel and a refrigerating medium output channel which are communicated with the refrigerating medium heat exchange cavity; the method is characterized in that: concave-convex structures are regularly arranged in the heat exchange areas of the first plate and the second plate along the longitudinal direction, and the concave-convex structures comprise ridges and grooves which are arranged at equal heights, and the concave-convex structures along the first plate and the second plate are mutually symmetrical along the joint surfaces of the first plate and the second plate; a refrigerant flow channel is formed between the first plate and the second plate below the first plate, and a secondary refrigerant flow channel is formed between the first plate and the second plate above the first plate; the cross-sectional area of the coolant flow passage is greater than the cross-sectional area of the coolant flow passage.
The utility model adopts the technical scheme, and the technical scheme relates to a plate heat exchanger with high-efficiency tooth shapes, which comprises a plurality of first plates and second plates, wherein a refrigerant heat exchange cavity and a secondary refrigerant heat exchange cavity are alternately formed between the first plates and the second plates; the first plate and the second plate are communicated and constructed with a refrigerant input channel, a refrigerant output channel, a secondary refrigerant input channel and a secondary refrigerant output channel. When the plate heat exchanger is used, the refrigerant flows into each refrigerant heat exchange cavity through the distribution holes from the refrigerant input channel and then is converged to the refrigerant output channel; the secondary refrigerant flows into and distributes into each secondary refrigerant heat exchange cavity from the secondary refrigerant input channel and then is converged to the secondary refrigerant output channel; the secondary refrigerant and the refrigerant exchange heat on two sides of the plate heat exchange plates.
On the basis, the scheme requires that the sectional area of the secondary refrigerant flow channel is larger than that of the refrigerant flow channel, and the scheme is suitable for the condition of small temperature difference before and after water side heat exchange, and has the advantages of large secondary refrigerant flow channel, smaller water resistance, smaller generated pressure drop and larger heat exchange area; the refrigerant flow channel is relatively small, so that the time of the refrigerant in the flow channel is prolonged, and the heat exchange efficiency is improved.
Further, the concave-convex structure on the heat exchange area of the first plate and the second plate in the scheme meets the following requirements:
1, adopting raised ridges and grooves which are arranged at equal heights;
2, the concave-convex structures of the first plate and the second plate are symmetrical to each other along the joint surfaces of the two plates.
Based on the two requirements, when a plurality of first plates and second plates are alternately stacked, the convex ridges and the concave grooves in the concave-convex structures of the two adjacent first plates and second plates are abutted together, so that the compressive strength of the plates is ensured.
In summary, the plate heat exchanger of the scheme constructs the secondary refrigerant flow channels and the refrigerant flow channels with different sectional areas on the basis of not reducing the strength of the plate, and is used for improving the heat exchange efficiency.
In a specific embodiment, when a plurality of first plates and second plates are alternately stacked, the upper end face of a first ridge of the first plate is attached to the lower end face of a second groove of the second plate above the first ridge; the upper end face of the second convex ridge of the second plate is attached to the lower end face of the first groove of the first plate above the second convex ridge. The first ridge of the first plate and the second groove of the second plate below the first ridge are combined to construct a refrigerant flow channel, and the second ridge of the second plate and the first groove of the first plate below the second ridge are combined to construct a secondary refrigerant flow channel.
In a specific embodiment, the ridge width of the first ridge of the first plate and the groove width of the second groove of the second plate are both a, and the ridge width of the first groove of the first plate and the ridge width of the second ridge of the second plate are both b, a < b. In the scheme, the ridge and the groove are respectively constructed on the first plate and the second plate in a mode of unequal widths, so that when a plurality of first plates and second plates are alternately stacked, the secondary refrigerant flow channels and the refrigerant flow channels with different sectional areas are formed.
In one embodiment, the relief structures are arranged in a zigzag or sine-cosine waveform.
In another embodiment, the first ridge and the second ridge are each constructed in a trapezoidal shape; when a plurality of first plates and a plurality of second plates are alternately stacked, the top of the first ridge is in surface contact with the bottom of the second groove, and the top of the second ridge is in surface contact with the bottom of the first groove. In this scheme, the first ridge and the second ridge are configured as trapezoids, and the concave-convex structures defining the first plate and the second plate in the above scheme are symmetrical to each other along the joint surfaces of the two plates, so that the first groove and the second groove are also trapezoidal. The convex ridges and the concave grooves in trapezoid shapes are in surface contact during lamination, so that the contact area is larger, and the strength of the plate is higher. And the heat exchange area is relatively larger when constructing the coolant flow channels and the refrigerant flow channels.
Drawings
Fig. 1 is a perspective view of a plate heat exchanger in a partially cut-away state.
Fig. 2 is an enlarged view of the section I of fig. 1.
Fig. 3 is a schematic illustration of the corrugation of the first plate.
Fig. 4 is a schematic illustration of the corrugation of the second plate.
Fig. 5 is a schematic flow passage diagram in a state where the first plate and the second plate are combined.
Detailed Description
Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present utility model and should not be construed as limiting the utility model.
In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.
In the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present utility model, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
As shown in fig. 1 to 5, the present embodiment relates to a plate heat exchanger having a high-efficiency tooth shape, which includes a plurality of first plates 1 and second plates 2 alternately stacked, and refrigerant heat exchange cavities and coolant heat exchange cavities are alternately formed between the first plates 1 and the second plates 2. The opposite end corners of the first plate 1 and the second plate 2 are respectively provided with a refrigerant inlet 101 and a refrigerant outlet 102, and a refrigerant inlet 103 and a refrigerant outlet 104. The refrigerant inlet 101 and the refrigerant outlet 102 on the first plate 1 and the second plate 2 are correspondingly connected to form a refrigerant input channel 105 and a refrigerant output channel 106 which are communicated with the refrigerant heat exchange cavity, and the secondary refrigerant inlet 103 and the secondary refrigerant outlet 104 are correspondingly connected to form a secondary refrigerant input channel 107 and a secondary refrigerant output channel 108 which are communicated with the secondary refrigerant heat exchange cavity. The plate heat exchanger comprises a plurality of first plates 1 and second plates 2, wherein a refrigerant heat exchange cavity and a secondary refrigerant heat exchange cavity are alternately formed between the first plates 1 and the second plates 2. The first plate 1 and the second plate 2 are communicated with each other to form a refrigerant input channel 105, a refrigerant output channel 106, a secondary refrigerant input channel 107 and a secondary refrigerant output channel 108. In use of the plate heat exchanger, refrigerant flows from the refrigerant inlet channel 105 through the distribution holes 109 into the respective refrigerant heat exchange cavities and then merges into the refrigerant outlet channel 106. The coolant flows from the coolant input channels 107 into the respective coolant heat exchange cavities for distribution, and then merges into the coolant output channels 108. The secondary refrigerant and the refrigerant exchange heat on two sides of the plate heat exchange plates.
In a further scheme, concave-convex structures are regularly arranged in the heat exchange areas of the first plate 1 and the second plate 2 along the longitudinal direction, the concave-convex structures comprise ridges and grooves which are arranged at equal heights, and the concave-convex structures along the first plate 1 and the second plate 2 are symmetrical to each other along the joint surfaces of the first plate 1 and the second plate 2. A refrigerant flow channel is formed between the first plate 1 and the second plate 2 below the first plate, and a secondary refrigerant flow channel is formed between the second plate 2 above the first plate. The cross-sectional area of the coolant flow passage is greater than the cross-sectional area of the coolant flow passage.
The scheme requires that the sectional area of the secondary refrigerant flow channel is larger than that of the refrigerant flow channel, and the scheme is suitable for the condition that the temperature difference before and after water side heat exchange is smaller, the secondary refrigerant flow channel is large, the water resistance is smaller, the generated pressure drop is smaller, and the heat exchange area is larger. The refrigerant flow channel is relatively small, so that the time of the refrigerant in the flow channel is prolonged, and the heat exchange efficiency is improved.
Further, the concave-convex structure on the heat exchanging area of the first plate 1 and the second plate 2 in the present solution meets the following requirements:
1, adopting the convex ridges and the concave grooves which are arranged at equal height.
2, the concave-convex structures of the first plate 1 and the second plate 2 are symmetrical to each other along the joint surfaces of the two.
Based on the two requirements, when a plurality of first plates 1 and second plates 2 are alternately stacked, the ridges and the grooves in the concave-convex structures of the adjacent two first plates 1 and second plates 2 are abutted together, so that the compressive strength of the plates is ensured.
In summary, the plate heat exchanger of the scheme constructs the secondary refrigerant flow channels and the refrigerant flow channels with different sectional areas on the basis of not reducing the strength of the plate, and is used for improving the heat exchange efficiency.
In the embodiment shown in fig. 2, when a plurality of first plates 1 and second plates 2 are stacked alternately, the upper end surfaces of the first ridges 11 of the first plates 1 are attached to the lower end surfaces of the second grooves of the second plates 2 above them. The upper end surface of the second ridge 21 of the second plate 2 is attached to the lower end surface of the first groove 12 of the first plate 1 above the second ridge. The first ridge 11 of the first plate 1 and the second groove 22 of the second plate 2 below the first ridge are combined to construct a refrigerant flow channel 100, and the second ridge 21 of the second plate 2 and the first groove 12 of the first plate 1 below the second ridge are combined to construct a secondary refrigerant flow channel 200.
In a specific embodiment, the ridge width of the first ridge 11 of the first plate 1 and the groove width of the second groove 22 of the second plate 2 are both a, and the groove width of the first groove 12 of the first plate 1 and the ridge width of the second ridge 21 of the second plate 2 are both b, a < b. In this embodiment, the ridge and the groove are respectively formed on the first plate 1 and the second plate 2 in a manner of unequal widths, so that the coolant flow channels 200 and the coolant flow channels 100 with different cross-sectional areas are formed when a plurality of first plates 1 and second plates 2 are alternately stacked.
In one embodiment, the relief structures are arranged in a zigzag or sine-cosine waveform.
In another embodiment shown in the figures, the first ridge 11 and the second ridge 21 are each constructed in a trapezoidal shape. When the plurality of first plates 1 and the plurality of second plates 2 are alternately stacked, the top of the first ridge 11 and the bottom of the second groove 22 are in surface contact, and the top of the second ridge 21 and the bottom of the first groove 12 are in surface contact. In this embodiment, the first ridge 11 and the second ridge 21 are configured in a trapezoid shape, and the first groove 12 and the second groove 22 are also configured in a trapezoid shape because the concave-convex structures defining the first plate 1 and the second plate 2 in the above embodiment are symmetrical to each other along the joint surfaces of the two. The convex ridges and the concave grooves in trapezoid shapes are in surface contact during lamination, so that the contact area is larger, and the strength of the plate is higher. And the heat exchange area is relatively larger when constructing the coolant flow channels 200 and the refrigerant flow channels 100.
The heat exchange plate adopting the scheme has the advantages that:
1. the grooves with different widths form channels with different areas, so that the device is suitable for the characteristics of different fluids at two sides of the plate exchange, and reduces the flow resistance; 2. because the channel on one side is enlarged, the contact area is increased, and meanwhile, the channels on two sides are asymmetrically designed, the turbulence of fluid is increased, and the flow is improved
The heat exchange performance is high;
3. the heights of the channels at the two sides are equal, so that the strength of the plate is improved compared with the existing design of high and low teeth;
in the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Although embodiments of the present utility model have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the utility model, and that variations, modifications, alternatives, and variations may be made in the above embodiments by those skilled in the art without departing from the spirit and principles of the utility model.
Claims (6)
1. A plate heat exchanger with high-efficiency tooth shape comprises a plurality of first plates (1) and second plates (2) which are alternately stacked, wherein a refrigerant heat exchange cavity and a secondary refrigerant heat exchange cavity are alternately formed between the first plates (1) and the second plates (2); the opposite end angles of the first plate (1) and the second plate (2) are respectively provided with a refrigerant inlet (101) and a refrigerant outlet (102), and a secondary refrigerant inlet (103) and a secondary refrigerant outlet (104); a refrigerant inlet (101) and a refrigerant outlet (102) on the first plate (1) and the second plate (2) are correspondingly connected to form a refrigerant input channel (105) and a refrigerant output channel (106) which are communicated with the refrigerant heat exchange cavity, and a secondary refrigerant inlet (103) and a secondary refrigerant outlet (104) are correspondingly connected to form a secondary refrigerant input channel (107) and a secondary refrigerant output channel (108) which are communicated with the secondary refrigerant heat exchange cavity; the method is characterized in that: concave-convex structures are regularly arranged in the heat exchange areas of the first plate (1) and the second plate (2) along the longitudinal direction, the concave-convex structures comprise ridges and grooves which are arranged at equal heights, and the concave-convex structures along the first plate (1) and the second plate (2) are mutually symmetrical along the joint surfaces of the two; a refrigerant flow channel (100) is formed between the first plate (1) and the second plate (2) below the first plate, and a secondary refrigerant flow channel (200) is formed between the first plate and the second plate (2) above the second plate; the cross-sectional area of the coolant flow channels (200) is greater than the cross-sectional area of the coolant flow channels (100).
2. A plate heat exchanger having a high efficiency tooth form as claimed in claim 1 wherein: when a plurality of first plates (1) and second plates (2) are alternately stacked, the upper end face of a first ridge (11) of the first plate (1) is attached to the lower end face of a second groove (22) of the second plate (2) above the first ridge; the upper end face of the second convex ridge (21) of the second plate (2) is attached to the lower end face of the first groove (12) of the first plate (1) above the second convex ridge.
3. A plate heat exchanger having a high efficiency tooth form as claimed in claim 2 wherein: the first ridge (11) of the first plate (1) is combined with the second groove (22) of the second plate (2) below the first ridge to form a refrigerant flow channel (100), and the second ridge (21) of the second plate (2) is combined with the first groove (12) of the first plate (1) below the second ridge to form a secondary refrigerant flow channel (200).
4. A plate heat exchanger having a high efficiency tooth form according to claim 3, wherein: the ridge width of the first ridge (11) of the first plate (1) and the groove width of the second groove (22) of the second plate (2) are both a, the groove width of the first groove (12) of the first plate (1) and the ridge width of the second ridge (21) of the second plate (2) are both b, and a is less than b.
5. A plate heat exchanger having a high efficiency tooth form according to any of claims 1-4, wherein: the relief structures are arranged in a zigzag or sine-cosine waveform.
6. A plate heat exchanger having a high efficiency tooth form according to any of claims 2-4, wherein: the first ridge (11) and the second ridge (21) are each constructed in a trapezoidal shape; when a plurality of first plates (1) and a plurality of second plates (2) are alternately stacked, the top of the first convex ridge (11) is in surface contact with the bottom of the second groove (22), and the top of the second convex ridge (21) is in surface contact with the bottom of the first groove (12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320802873.9U CN220472395U (en) | 2023-04-12 | 2023-04-12 | Plate heat exchanger with high-efficient profile of tooth |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320802873.9U CN220472395U (en) | 2023-04-12 | 2023-04-12 | Plate heat exchanger with high-efficient profile of tooth |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220472395U true CN220472395U (en) | 2024-02-09 |
Family
ID=89805283
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202320802873.9U Active CN220472395U (en) | 2023-04-12 | 2023-04-12 | Plate heat exchanger with high-efficient profile of tooth |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN220472395U (en) |
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2023
- 2023-04-12 CN CN202320802873.9U patent/CN220472395U/en active Active
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