CN210154385U

CN210154385U - Heat exchanger

Info

Publication number: CN210154385U
Application number: CN201920096972.3U
Authority: CN
Inventors: 不公告发明人
Original assignee: Zhejiang Sanhua Automotive Components Co Ltd
Current assignee: Zhejiang Sanhua Automotive Components Co Ltd
Priority date: 2019-01-21
Filing date: 2019-01-21
Publication date: 2020-03-17
Anticipated expiration: 2029-01-21

Abstract

The utility model discloses a heat exchanger, the heat exchanger includes first circulation passageway, second circulation passageway, first circulation passageway with special through first fin and second fin is placed in the second circulation passageway, makes the heat exchanger compromise heat exchange efficiency and pressure drop simultaneously.

Description

Heat exchanger

Technical Field

The utility model relates to a heat exchange equipment technical field.

Background

The plate heat exchanger can be used for heat exchange of two fluids under general conditions, the flowing pressure drop of the fluids with different viscosities in the heat exchanger with the same structure can be different, and meanwhile, the heat exchange efficiency of the fluids is always an important index of the plate heat exchanger, so that the heat exchange efficiency and the pressure drop are considered, and the plate heat exchanger is difficult to solve.

SUMMERY OF THE UTILITY MODEL

In order to solve the technical problem, the technical scheme of the utility model provides a heat exchanger.

A heat exchanger comprising a plurality of plates arranged in a stack, the plates comprising a plurality of first plates and a plurality of second plates, the heat exchanger comprising a first flow-through channel and a second flow-through channel, the first and second flow-through channels being located between adjacent first and second plates, the first flow-through channel being non-communicating with the second flow-through channel, the plates comprising at least a first porthole, a second porthole, a third porthole, a fourth porthole, the first porthole being in communication with the first flow-through channel, the second porthole being in communication with the second flow-through channel, the third porthole being in communication with the second flow-through channel, the fourth porthole being in communication with the second flow-through channel;

the heat exchanger comprises a first fin and a second fin, the first fin is located between the first plate and the second plate, the second fin is located between the first plate and the second plate, the first fin is located in the first flow channel, and the second fin is located in the second flow channel; defining the direction of a connecting line of a first hole and a second hole of the plate as a first plate direction, and defining the direction of a connecting line of a third hole and a fourth hole of the plate as a second plate direction;

the first fin comprises a plurality of first protruding portions and a plurality of first base portions, the first protruding portions protrude relative to the first base portions, the first fin comprises a first fin length direction, the first protruding portions extend towards the first fin length direction, and an angle formed by the first plate sheet direction and the first fin length direction is smaller than or equal to 40 degrees;

the second fin comprises a plurality of second bases and a plurality of second protrusions, the second protrusions are opposite to the second bases and protrude, the second fin comprises a second fin length direction, the second protrusions extend towards the second fin length direction, and the angle between the second plate sheet direction and the second fin length direction is larger than 50 degrees.

The technical scheme of the utility model through the above setting of fin, make the heat exchanger can compromise heat exchange efficiency and pressure drop simultaneously.

Drawings

Fig. 1 is an overall schematic view of an embodiment of the heat exchanger of the present invention.

Fig. 2 is a schematic cross-sectional view of the heat exchanger shown in fig. 1.

Fig. 3 is a partially enlarged view of the cross-sectional view of fig. 2.

Figure 4 is a schematic view of a first or second plate of one embodiment of the heat exchanger shown in figure 1.

FIG. 5 is a schematic view of one embodiment of a first fin or a second fin of the heat exchanger shown in FIG. 1.

Fig. 6 is a partial enlarged view of the fin shown in fig. 5.

FIG. 7 is a schematic view of another embodiment of a first fin or a second fin of the heat exchanger shown in FIG. 1.

FIG. 8 is a schematic view of a third plate.

Fig. 9 is a schematic view of a fourth plate.

Fig. 10 is a schematic view of a fifth plate.

Detailed Description

Specific embodiments will now be described in detail with reference to the accompanying drawings. In the following detailed description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. Those skilled in the art will appreciate that the specific components, devices, and features illustrated in the accompanying drawings and described herein are merely exemplary and should not be considered as limiting.

Figure 1 illustrates a heat exchanger 10. the heat exchanger 10 comprises a heat exchanger core 11, a first side plate 12, a second side plate 13, a first foraminous member 14, a second foraminous member 15, a third foraminous member 16, and a fourth foraminous member 17. The two sides of the heat exchanger core 11 are respectively welded and fixed with the first side plate 12 and the second side plate 13.

The first tunnel-equipped member 14, the second tunnel-equipped member 15, the third tunnel-equipped member 16, and the fourth tunnel-equipped member 17 are all members with through holes, and may be all pipes, all blocks with through holes, a part of pipes, a part of blocks with through holes, or other forms of tunnel-equipped members.

Referring to fig. 2 and 3, the heat exchanger core 11 includes a plurality of stacked plates, the heat exchanger core 11 includes a plurality of first plates 111 and second plates 112, the first plates 111 and the second plates 112 are stacked to form first flow channels 41 and second flow channels 42, except for the two plates closest to each other, the first flow channels 41 and the second flow channels 42 are respectively disposed on two sides of a plurality of plates, for example, one of the first plate and the two second plates adjacent to the first plate form the first flow channels 41, and the other second plate forms the second flow channels 42, and the first flow channels 41 are not communicated with the second flow channels 42.

When the heat exchanger 10 is in an operating state, the heat exchange media flowing in the heat exchanger 10 include a first heat exchange medium and a second heat exchange medium, the first heat exchange medium flows in the first circulation passage 41, the second heat exchange medium flows in the second circulation passage 42, the viscosity of the first heat exchange medium is greater than that of the second heat exchange medium, for example, the first heat exchange medium is a coolant, and the second heat exchange medium is a refrigerant. Therefore, under the same test conditions, the pressure drop of the first heat exchange medium is larger than that of the second heat exchange medium when the flow paths are consistent.

The first plate 111 and the second plate 112 are substantially the same structure. For ease of understanding, only one of the first and

second plates

111, 112, 20, will be described in detail below, as shown in fig. 4.

The plate 20 is of an approximately rectangular configuration, the plate 20 comprising a plate plane 21 and a flange 22, the flange 22 being located at the periphery of the plate plane 21.

The first plate 111 and the second plate 112 each comprise a first porthole 23, a second porthole 24, a third porthole 25 and a fourth porthole 26, the first portholes 23 on each plate are aligned to form a first channel, the second portholes 24 on each plate are aligned to form a second channel, the third portholes 25 on each plate are aligned to form a third channel, and the fourth portholes 26 on each plate are aligned to form a fourth channel. The first hole passage of the heat exchanger core 11 is communicated with the first circulation passage, the second hole passage is communicated with the first circulation passage, the third hole passage is communicated with the second circulation passage, and the fourth hole passage is communicated with the second circulation passage.

Two concave platforms 231 which are sunken to a certain depth in the plate plane 21 are formed at two positions of the plate plane 21 close to the corners, the concave platforms 231 are provided with a first hole 23 and a second hole 24, two bosses 232 which are protruded to a certain height in the plate plane 21 are formed at the other two positions of the plate plane 21 close to the corners, and the bosses 232 are provided with a third hole 25 and a fourth hole 26. The first and

second ports

23, 24 may be located on the same side or diagonal side of the plate 20, and fig. 4 shows that the first and

second ports

23, 24 are located on the same side of the plate 20. The third aperture 25 and the fourth aperture 26 may likewise be located on the same side or on diagonal sides of the plate 20. When the adjacent plates are laminated together, a part of the burring between the first plate 111 and the second plate 112 is in close abutment with each other.

The central connecting line of the first port 23 and the second port 24 of the plate 20 is defined as the first plate direction, and the central connecting line of the third port 25 and the fourth port 26 of the plate 20 is defined as the second plate direction. The heat exchanger first direction and the heat exchanger second direction may be parallel. For example, in fig. 4 the first port 23 is located on the same side of the plate 20 as the second port 24, and the third port 25 is located on the same side of the plate 20 as the fourth port 26, the first plate orientation being shown by the double-headed arrow D1 in fig. 4, and the second plate orientation being shown by the double-headed arrow D2 in fig. 4.

The heat exchanger core 11 includes a first fin 30 and a second fin, the first fin 30 is located between the first plate 111 and the second plate 112, the second fin is located between the first plate 111 and the second plate 112, the first fin 30 is disposed in the first circulation channel, and the second fin is disposed in the second circulation channel.

The first fin 30 comprises a plurality of first base parts 34 and a plurality of first protruding parts 32, the first protruding parts 32 protrude relative to the first base parts 34, the first fin 30 comprises a first fin length direction, and as shown by a double-headed arrow E in fig. 5 or fig. 7, the first protruding parts 32 are arranged to extend in the first fin length direction; spaced adjacent the first boss 32 and spaced adjacent the first base 34.

The first flow channel 41 includes a first sub-channel 51 and a second sub-channel 52, the first sub-channel 51 is located between the first protrusion 32 and the second plate 112, the second sub-channel 52 is located between the first base 34 and the first plate 111, the first sub-channel 51 extends in the first fin longitudinal direction, and the second sub-channel 52 extends in the first fin longitudinal direction.

The second fins comprise a plurality of second base parts and a plurality of second protruding parts, the second protruding parts protrude relative to the second base parts, the second fins comprise second fin length directions, and the second protruding parts extend towards the second fin length directions approximately; the adjacent second bulge is arranged at intervals, and the adjacent second base is arranged at intervals.

The second flow channel 42 includes a third sub-channel and a fourth sub-channel, the third sub-channel is located between the second protruding portion and the first plate, the fourth sub-channel is located between the second base portion and the second plate, the third sub-channel extends in the second fin length direction, and the fourth sub-channel extends in the second fin length direction.

The height direction is defined as the stacking direction of the sheets, as indicated by the double-headed arrow H in fig. 1.

Fig. 5 is an embodiment of the first fin 30, and fig. 6 is a partial enlarged view of the fin shown in fig. 5.

The first protruding portion 32 includes a plurality of first protruding units 31, and adjacent first protruding units 31 of the same first protruding portion 32 are arranged in a staggered manner. The first protrusion unit 31 includes a first top portion 33 and at least two first side portions 35, the first side portions 35 extend in the height direction from the first base portion 34, and the two first side portions 35 of the first protrusion unit 31 are spaced apart from each other. A window 37 is left between two adjacent first boss units 31 of the same first boss 32. The first sub-channel 51 is disposed between the first side portions of the first protrusion units, and the second sub-channel 52 is disposed between the first side portions of the adjacent first protrusion units.

Fig. 7 shows another embodiment of the first fin 30, wherein the first protrusion 32 includes a first top portion 33 and at least two first side portions 35, the first side portions 35 extend in the height direction from the first base portion 34, and the first side portions of the first protrusion are spaced apart from each other. The first side 35 of the first protrusion 32 includes a number of through holes 38, and the specific number and size of the through holes 38 can be determined according to the length of the first protrusion 32 and the flow resistance requirement. The first sub-channel 51 is disposed between the first side portions of the first protruding portions, and the second sub-channel 52 is disposed between the first side portions of the adjacent first protruding portions.

When the first heat exchange medium flows to the first fins 30 along the length direction of the first fins, that is, the direction of the solid arrows in fig. 6 or fig. 7, although the first fins 30 have a certain disturbance effect on the first heat exchange medium, most areas of the first fins 30 are on the parallel surfaces in the flow direction, only a small number of thickness cross sections are perpendicular to the flow direction, the flow resistance is mainly caused by the friction on the surfaces of the fins, so the friction resistance is small, and the disturbance effect of the first fins 30 on the first heat exchange medium is also weak.

The second fin may adopt a structure identical to that of the first fin 30, but the arrangement manner of the second fin in the heat exchanger is not identical to that of the first fin 30 in the heat exchanger, for example, both the first fin 30 and the second fin are in the structure shown in fig. 5, but the length direction of the first fin 30 arranged in the first flow channel is 90 ° to that of the second fin arranged in the second flow channel. Of course, the second fin may have a structure different from that of the first fin 30, for example, when the first fin 30 is the fin shown in fig. 5, the second fin is the fin shown in fig. 7.

The fin shown in fig. 5 was used as the second fin, and an appropriate placement angle was selected. When the second heat exchange medium flows to the second fins in the direction of the dotted line in fig. 6, part of the second heat exchange medium is first hindered by the second side of the second protruding unit to continuously generate a flow split in the transverse plane. The second heat exchange medium after shunting can mix with the second heat exchange medium of not shunting and pass through the second protruding unit in back, and at this moment, the second heat exchange medium receives the hindrance once more and produces the reposition of redundant personnel on the transverse plane, and finally, almost all second heat exchange medium all can pass through the window between the adjacent second protruding unit. In the process of shunting the second heat exchange medium, the boundary layer of the second heat exchange medium is continuously damaged by the fins, so that disturbance on a local plane can be generated, the heat exchange capability of the heat exchanger 10 is enhanced to a certain degree, and meanwhile, the flow resistance is large.

As another embodiment, the heat exchanger core 11 may further include at least one third plate 113 and one fourth plate 114, and the third plate 113 and the fourth plate 114 may be mostly structured with reference to the first plate 111 and the second plate 112. As shown in fig. 8, the third plate 113 includes the first blocking portion 19a and the second, third, and

fourth orifices

24, 25, and 26. As shown in fig. 9, the fourth plate 114 includes a first port 23, a second port 24, a third barrier 19b, and a fourth port 26, the second port 24 of the third plate 113 and the second port 24 of the fourth plate 114 are aligned with the second port 24 of the first plate 111 and the second port 24 of the second plate 112 to form a second hole, and the fourth port 26 of the third plate 113 and the fourth port 26 of the fourth plate 114 are aligned with the fourth port 26 of the first plate 111 and the fourth port 26 of the second plate 112 to form a fourth hole. The first blocking portion 19a is located at a position where the third plate 113 corresponds to the first port 23 of the first plate 111 and the second plate 112, the first hole channel of the heat exchanger core 11 is divided into at least two sub-hole channels by the first blocking portion 19a, the first flow channel 41 is divided into at least two heat exchange sections by the third plate 113, and the flow directions of fluids in the two heat exchange sections are opposite; the third blocking portion 19b is located at a position of the fourth plate 114 corresponding to the third port 25 of the first and

second plates

111 and 112, the third port of the heat exchanger core 11 is divided into at least two sub-ports by the third blocking portion 19b, and the second flow-through channel 42 is divided into at least two heat exchange sections by the fourth plate 114, wherein the flow directions of the fluids in the two heat exchange sections are opposite. The heat exchanger core is divided into at least two heat exchange sections by the first blocking part 19a and the third blocking part 19b, which is beneficial to increasing the flow path of fluid and ensuring that the heat exchange device has better heat exchange performance under the condition of keeping the structure of the heat exchange device smaller. When one of the first heat exchange medium and the second heat exchange medium flows in from the pipeline arranged on the first side plate 12 and the other flows in from the pipeline arranged on the second side plate 13, the first heat exchange medium and the second heat exchange medium are in full countercurrent, and the heat exchange efficiency is better.

As another embodiment, the presence of the third plate 113 in the heat exchanger core 11 does not present the fourth plate 114 or the presence of the fourth plate 114 does not present the third plate 113.

As another embodiment, a fifth plate 115 is present in the heat exchanger core 11, and the structure of the fifth plate 115 can be mostly referred to the first plate 111 and the second plate 112. As shown in fig. 10, the fifth plate 115 includes a first stopper 19a ', a second orifice 24, a third stopper 19 b', and a fourth orifice 26. The first blocking portion 19a 'is located at a position of the fifth plate 115 corresponding to the first port 23 of the first plate 111 and the second plate 112, the first hole channel of the heat exchanger core 11 is divided into at least two sub-hole channels by the first blocking portion 19 a', the first flow channel 41 is divided into at least two heat exchange sections by the fifth plate 115, and the flow directions of the fluids in the two heat exchange sections are opposite; the third blocking portion 19b 'is located at a position of the fifth plate 115 corresponding to the third port 25 of the first and

second plates

111 and 112, the third hole channel of the heat exchanger core 11 is divided into at least two sub-hole channels by the third blocking portion 19 b', and the second flow-through channel 42 is divided into at least two heat exchange sections by the fifth plate 115, wherein the flow directions of the fluids in the two heat exchange sections are opposite.

The third plate 113 has substantially the same structure as the first plate 111 or the second plate 112, and the third plate 113 forms the first blocking portion 19a without forming an opening at a position corresponding to a boss or a concave corresponding to the first opening formed in the first plate 111 or the second plate 112. The fourth plate 114 has substantially the same structure as the first plate 111 or the second plate 112, and the third blocking portion 19b is formed in the fourth plate 114 at a position corresponding to a boss or a recess where the third aperture is formed in the first plate 111 or the second plate 112 without forming an aperture. The fifth plate 115 has substantially the same structure as the first plate 111 or the second plate 112, and the fifth plate 115 forms a first blocking portion 19 a' without forming an orifice at a position corresponding to a boss or a concave platform of the first orifice formed on the first plate 111 or the second plate 112; the fifth plate 115 forms a second blocking portion 19 b' without forming an opening at a position corresponding to the boss or the concave platform of the first plate or the second plate 112 provided with the third opening.

The angle formed by the first plate direction and the length direction of the first fins is less than or equal to 40 degrees, and the angle formed by the second plate direction and the length direction of the second fins is more than 50 degrees.

Further, when the angle between the first plate direction and the first fin length direction is less than or equal to 30 degrees, and the angle between the second plate direction and the second fin length direction is greater than 60 degrees, compared with the case that the angle between the first plate direction and the first fin length direction is 40 degrees, the angle between the second plate direction and the second fin length direction is 50 degrees, the flow resistance of the first heat exchange medium in the first circulation channel is smaller, the flow resistance of the second heat exchange medium in the second circulation channel is larger, and the turbulent flow effect of the second heat exchange medium in the second circulation channel is more obvious.

Further, when the angle formed by the direction of the first plate and the length direction of the first fin is 0 degree and the angle formed by the direction of the second plate and the length direction of the second fin is 90 degrees, the flow resistance of the first heat exchange medium in the first circulation channel is minimum, the flow resistance of the second heat exchange medium in the second circulation channel is maximum, and the turbulent flow effect of the second heat exchange medium in the second circulation channel is most obvious.

The different arrangement modes of the first fins 30 and the second fins in the first circulation channels 41 and the second circulation channels 42, the first heat exchange medium with higher viscosity flowing through the first circulation channels 41, and the second heat exchange medium with lower viscosity flowing through the second circulation channels 42 can make the heat exchange performance of the first heat exchange medium side better, and the pressure drop of the second heat exchange medium side not too large.

It should be noted that: the expressions in the above embodiments with respect to "first", "second", "third", "fourth", and the like are merely for naming purposes and do not include any sequential limitations. The above embodiments are only used for illustrating the present invention and not for limiting the technical solutions described in the present invention, and although the present invention has been described in detail with reference to the above embodiments, it should be understood by those skilled in the art that the technical solutions and modifications thereof without departing from the spirit and scope of the present invention can be modified or replaced by other technical solutions and modifications by those skilled in the art.

Claims

1. A heat exchanger comprising a plurality of plates arranged in a stack, the plates comprising a plurality of first plates and a plurality of second plates, the heat exchanger comprising a first flow-through channel and a second flow-through channel, the first and second flow-through channels being located between adjacent first and second plates, the first flow-through channel being non-communicating with the second flow-through channel, the plates comprising at least a first porthole, a second porthole, a third porthole, a fourth porthole, the first porthole being in communication with the first flow-through channel, the second porthole being in communication with the second flow-through channel, the third porthole being in communication with the second flow-through channel, the fourth porthole being in communication with the second flow-through channel; the method is characterized in that:

2. The heat exchanger of claim 1, wherein the first flow channel comprises a first sub-channel and a second sub-channel, the first sub-channel being located between the first boss and the second plate, the second sub-channel being located between the first base and the first plate, the first sub-channel extending toward the first fin length direction, the second sub-channel extending toward the first fin length direction.

3. The heat exchanger of claim 2, wherein the first bosses comprise a plurality of first boss units, adjacent first boss units of the first bosses are staggered, the first boss units comprise a first top portion, at least two first side portions, and the two first side portions are spaced apart;

defining the stacking direction of the plate pieces as a height direction, wherein the first side part extends from the first base part to the height direction;

the first sub-channel is arranged between the first side parts of the first protrusion units, and the second sub-channel is arranged between the first side parts of the adjacent first protrusion units.

4. The heat exchanger of claim 2, wherein the first boss includes a first top portion, a first side portion, the first side portion of the first boss being spaced apart;

the first sub-channel is arranged between the first side parts of the first protruding parts, and the second sub-channel is arranged between the first side parts of the adjacent first protruding parts.

5. The heat exchanger according to claim 2 or 3, wherein the second flow channel comprises a third sub-channel and a fourth sub-channel, the second protrusion comprises a plurality of second protrusion units, adjacent second protrusion units of the second protrusion are arranged in a staggered manner, a window is left between adjacent second protrusion units of the second protrusion, and the second protrusion units comprise a second top part and a second side part;

the third sub-channel is arranged between the second side parts of the second protrusion units, and the fourth sub-channel is arranged between the second side parts of the adjacent second protrusion units.

6. The heat exchanger of claim 2 or 4, wherein the second flow channel comprises a third sub-channel and a fourth sub-channel, the second boss comprises a second top portion, a second side portion, and the second side portion comprises a number of through holes;

the third sub-channel is arranged between the second side portions of the second protruding portions, and the fourth sub-channel is arranged between the second side portions of the adjacent second protruding units.

7. The heat exchanger of claim 1, wherein the heat exchanger comprises a third plate, the third plate comprises a first blocking portion, a second port, a third port, and a fourth port, the second port of the third plate is aligned with the second port of the first plate and the second port of the second plate to form a second port, the third port of the third plate is aligned with the third port of the first plate and the third port of the second plate to form a third port, the fourth port of the third plate is aligned with the fourth port of the first plate and the fourth port of the second plate to form a fourth port, and the first blocking portion of the third plate is located at a position corresponding to the first port of the first plate and the first port of the second plate.

8. The heat exchanger of claim 7, comprising a fourth plate comprising a first port aligned with the first port of the first plate and the first port of the second plate to form a first porthole, a second port aligned with the second port of the first plate and the second port of the second plate to form a second porthole, a third barrier aligned with the fourth port of the first plate and the fourth port of the second plate to form a fourth porthole, and a fourth barrier located at a position corresponding to the third port of the first plate or the second plate.

9. The heat exchanger according to claim 1 or 2 or 3 or 4 or 7 or 8, wherein the first plate direction makes an angle of 30 ° or less with the first fin length direction; the angle formed by the direction of the second plate and the length direction of the second fin is larger than 60 degrees.

10. The heat exchanger of claim 5, wherein the first plate direction makes an angle of 30 ° or less with the first fin length direction; the angle formed by the direction of the second plate and the length direction of the second fin is larger than 60 degrees.

11. The heat exchanger of claim 6, wherein the first plate direction makes an angle of 30 ° or less with the first fin length direction; the angle formed by the direction of the second plate and the length direction of the second fin is larger than 60 degrees.

12. The heat exchanger according to claim 1 or 2 or 3 or 4 or 7 or 8, wherein the first plate direction makes an angle of 0 ° with the first fin length direction; the angle formed by the direction of the second plate and the length direction of the second fin is 90 degrees.

13. The heat exchanger of claim 5, wherein the first plate direction is at an angle of 0 ° to the first fin length direction; the angle formed by the direction of the second plate and the length direction of the second fin is 90 degrees.

14. The heat exchanger of claim 6, wherein the first plate direction is at an angle of 0 ° to the first fin length direction; the angle formed by the direction of the second plate and the length direction of the second fin is 90 degrees.