CN211953808U

CN211953808U - Plate heat exchanger with asymmetric passageway

Info

Publication number: CN211953808U
Application number: CN202020379086.4U
Authority: CN
Inventors: 施吉璐; 韩维哲; 陈天鹏; 戚邗云; 张雯
Original assignee: Weal Yield Jiangsu Heat Exchanger Co ltd
Current assignee: Weal Yield Jiangsu Heat Exchanger Co ltd
Priority date: 2020-03-23
Filing date: 2020-03-23
Publication date: 2020-11-17
Anticipated expiration: 2030-03-23

Abstract

The utility model belongs to the technical field of the heat exchanger technique and specifically relates to a plate heat exchanger with asymmetric passageway, including a plurality of range upon range of setting with the heat transfer slab that forms the heat transfer passageway, the heat transfer slab is first slab and the second slab that sets up in turn, and first slab and second slab all include main panel and baffle on every side, are equipped with a plurality of convex ridge on the main panel, form the valley between the adjacent convex ridge, and evenly distributed a plurality of recess on the valley of first slab makes the both sides of second slab form the asymmetric passageway that the volume is different. The utility model discloses a heat exchanger sets up a plurality of evenly distributed's recess on the valley of first slab, makes the both sides of second slab form the different asymmetric passageway of volume, increases heat transfer performance, and the setting of recess makes the convex ridge card of second slab establish between two adjacent recesses, and the convex ridge both sides inclined plane and the recess both sides inclined plane of mutual contact have effectively increased welding area, and the pressure-bearing effect of reinforcing heat exchanger makes heat transfer performance and pressure-bearing effect compromise.

Description

Plate heat exchanger with asymmetric passageway

Technical Field

The utility model belongs to the technical field of the heat exchanger technique and specifically relates to a plate heat exchanger with asymmetric passageway.

Background

The brazed plate heat exchanger is one efficient heat exchanger produced through brazing and includes one series of corrugated metal sheets. The various plates form channels between them through which heat is exchanged. Compared with the conventional shell-and-tube heat exchanger, the heat transfer coefficient of the heat exchanger is much higher under the condition of the same flow resistance and pump power consumption, and the heat exchanger tends to replace the shell-and-tube heat exchanger in an applicable range.

The heat exchange performance and the pressure bearing performance of the brazing plate type heat exchanger are two important technical indexes of products. On the premise of ensuring the design working condition of a client, the heat exchange performance of the heat exchanger is improved as much as possible and the pressure bearing effect of the heat exchanger is ensured. In the traditional brazing plate type heat exchanger, if the brazing plate type heat exchanger has the equal-height corrugation, the number of welding spots on the upper side and the lower side of each plate sheet is as large as that of welding spots on the upper side and the lower side of each plate sheet, so that the pressure bearing capacity can be ensured, but under the condition of the traditional equal-height corrugation, the volume of each channel is also the same, and the heat exchange effect is not; if traditional height buckled plate, although can form asymmetric passageway, can improve heat transfer effect, nevertheless because the solder joint quantity of both sides is not the same many about the slab, lead to the pressure-bearing effect variation of the few one side of solder joint easily. It can be seen that the welding effect between the plates of the traditional brazed plate heat exchanger is often in inverse proportion to the heat exchange performance of the plates, the two can not be considered at the same time, and the pressure bearing performance of the traditional brazed plate heat exchanger is usually only dependent on the arrangement of the front end plate, the rear end plate and the reinforcing plate. On the premise of seeking to improve the heat exchange performance of the heat exchanger, a feasible research direction is provided by considering how to ensure the pressure-bearing effect from the structure of the heat exchanger plate.

SUMMERY OF THE UTILITY MODEL

In order to solve the problem that current plate heat exchanger's heat transfer performance and pressure-bearing effect can't be compromise, the utility model provides a plate heat exchanger with asymmetric passageway, this heat exchanger is through setting up a plurality of evenly distributed's recess on the valley of first slab, the both sides that make the second slab form the asymmetric passageway that the volume is different, heat transfer performance is increased, and the setting of recess makes the convex ridge of second slab be located between two adjacent recesses, mutual contact's convex ridge both sides inclined plane has effectively increased welding area with recess both sides inclined plane, the pressure-bearing effect of heat exchanger has been strengthened, make heat transfer performance and pressure-bearing effect compromise.

The utility model provides a technical scheme that its technical problem adopted is:

the utility model provides a plate heat exchanger with asymmetric passageway, includes a plurality of range upon range of setting in order to form the heat transfer slab of heat transfer passageway, the heat transfer slab is first slab and the second slab of alternative setting, first slab and second slab all include main panel and baffle on every side, be equipped with a plurality of convex ridge on the main panel, form the valley between the adjacent convex ridge, a plurality of recess of evenly distributed on the valley of first slab makes the asymmetric passageway of volume difference is formed to the both sides of second slab.

Preferably, the ridge of the second plate is clamped between two adjacent grooves of the first plate, so that the top of the ridge of the second plate is in contact with the bottom of the valley of the first plate, the upper ends of two sides of the ridge of the second plate are in contact with the side surfaces of the grooves of the first plate, and the contact part forms a welding point.

Preferably, the ridges are arranged in a fishbone shape from both axial sides of the first plate or the second plate.

Preferably, the second plate is rotated 180 ° with respect to the first plate.

Preferably, the valleys of the first plate have grooves at the central axis, and the rest of the grooves are uniformly distributed from the grooves at the central axis to two sides.

Preferably, the height of the ridges is 1.1 to 8 times the depth of the grooves.

Preferably, the height of the ridges is 2 to 4 times the depth of the grooves.

Preferably, four corners of the main panel have four corner holes, and the first plate has no recess provided in a valley of a portion thereof adjacent to the corner holes.

Preferably, the width of the main panel of the first plate is w1, the width of the main panel is w2, and w2 is 8-12 times of w 1.

The utility model has the advantages that:

(1) the heat exchanger of the utility model has the advantages that the grooves which are uniformly distributed are arranged on the valleys of the first plate, so that the two sides of the second plate form asymmetric channels with different volumes, the flowing pressure drop of the medium in the channel at the side with smaller volume is increased, the turbulence degree of the medium is obviously improved, the heat transfer effect of the medium in the heat exchanger is enhanced, and the heat exchange performance is obviously improved;

(2) the utility model discloses the setting of well recess makes the convex ridge card of second slab establish between two adjacent recesses on first slab, on the traditional slab that does not set up the recess, can only weld at the convex ridge top of second slab and the contact surface of the valley bottom of first slab, and welding area is less, and the utility model discloses except the contact surface of convex ridge top and valley bottom, contact area has still effectively been increased in convex ridge both sides inclined plane and recess both sides inclined plane department, under the prerequisite that does not change solder joint quantity promptly, has effectively increased the contact area of every solder joint, increases the atress ability of every solder joint, improves the holistic bearing capacity of heat exchanger, promptly the utility model discloses make heat transfer performance and bearing effect obtain taking into account;

(3) the utility model discloses a first slab does not set up the recess on the part valley that is close to the corner hole, and at the part that does not set up the recess, the passageway has great volume, can make the medium carry out quick water conservancy diversion, guarantees that the medium carries out quick, even distribution, does benefit to the medium and circulates more evenly in whole passageway, further improves heat transfer performance, guarantees permanent heat exchange stability.

Drawings

The present invention will be further explained with reference to the drawings and examples.

FIG. 1 is a schematic view of the arrangement of the heat exchange plates of the present invention;

FIG. 2 is a front view of a plate stack consisting of a first plate, a second plate and a first plate arranged in a stacked arrangement in that order;

FIG. 3 is a sectional view taken along line A-A in FIG. 2 (omitted view);

FIG. 4 is a sectional view (omitted view) taken along line B-B in FIG. 2;

FIG. 5 is an enlarged view of portion C of FIG. 2;

FIG. 6 is a front view (omitted view) of the second plate;

in the figure: 1. a first sheet; 2. a second sheet; 3. a main panel; 31. a raised ridge; 32. a valley; 321. a groove; 33. corner holes; 4. and a baffle plate.

Detailed Description

The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic drawings and illustrate the basic structure of the present invention only in a schematic manner, and thus show only the components related to the present invention.

A plate heat exchanger with asymmetric channels is disclosed, as shown in fig. 1, fig. 2, fig. 3, fig. 5 and fig. 6, which comprises a plurality of heat exchange plates stacked to form heat exchange channels, the heat exchange plates are first plates 1 and second plates 2 arranged alternately, each of the first plates 1 and the second plates 2 comprises a main panel 3 and a surrounding baffle 4, the main panel 3 is provided with a plurality of ridges 31, valleys 32 are formed between adjacent ridges 31, and a plurality of grooves 321 are uniformly distributed on the valleys 32 of the first plates 1, so that two sides of the second plates 2 form asymmetric channels with different volumes. As shown in the right part of fig. 3 with the groove 321, the volume of the channel formed on the second plate 2 is significantly smaller than that of the channel formed below, and in the asymmetric channel formed on both sides of the second plate, the flow pressure drop of the medium in the channel on the side with smaller volume is increased, and the turbulence degree of the medium is significantly improved, so that the heat transfer effect of the medium in the heat exchanger is enhanced, and the heat exchange performance is significantly improved. Generally, the channels with smaller volumes carry the refrigerant.

In a specific embodiment, as shown in fig. 4, the ridge 31 of the second plate 2 is clamped between two adjacent grooves 321 on the first plate 1, so that the top of the ridge 31 of the second plate 2 contacts the bottom of the valley 32 of the first plate 1, the upper ends of both sides of the ridge 31 of the second plate 2 contact the sides of the groove 321 of the first plate 1, and the contact part forms a welding point.

On the traditional slab that does not set up the recess, can only weld at the convex ridge top of second slab and the contact surface of the valley bottom of first slab, welding area is less, and the utility model discloses except the contact surface of convex ridge top and valley bottom, still effectively increased contact area in convex ridge both sides inclined plane and recess side inclined plane department, under the prerequisite that does not change solder joint quantity promptly, effectively increased the contact area of every solder joint, increased the atress ability of every solder joint, improved the holistic bearing capacity of heat exchanger, simultaneously because solder joint quantity is unchangeable, heat transfer area is not influenced, promptly the utility model discloses make heat transfer performance and pressure-bearing effect obtain taking into account.

In a particular embodiment, the ridges 31 are arranged as a fishbone from the central axial side of the first plate 1 or the second plate 2, as shown in fig. 1.

In a particular embodiment, as shown in fig. 1, the second plate 2 is rotated 180 ° with respect to the first plate 1.

In a specific embodiment, as shown in fig. 2, the valleys 32 of the first plate 1 have grooves 321 at the central axis position, and the other grooves 321 are uniformly arranged from the grooves 321 at the central axis position to both sides.

In a specific embodiment, the height of the ridges 31 is 1.1-8 times the depth of the grooves 321. In the specific embodiment, the depth of the groove 321 can be adjusted according to actual requirements, and it is feasible as long as the channel is not blocked.

In a particular embodiment, the height of the ridges 31 is 2-4 times the depth of the grooves 321. When the height of the ridge 31 is 2-4 times of the depth of the groove 321, better heat exchange effect and pressure bearing effect can be obtained, and 2 times, 2.5 times, 3 times, 3.5 times, 4 times and the like can be selected in specific embodiments.

In a specific embodiment, as shown in fig. 2, four corner holes 33 are formed at four corners of the main panel 3, and the first plate 1 is not provided with the grooves 321 on the part of the valleys 32 adjacent to the corner holes 33.

As shown in fig. 3, the first plate is not provided with grooves on the part of the valleys close to the angular holes, for the passage above the second plate 2: the part that does not set up the recess (lean on the left position in fig. 3, the volume of each passageway of this position equals) is bigger than the volume of the passageway that the part that sets up the recess (rightmost side in fig. 3, the volume of a passageway is less than the volume of a passageway below above this department) formed, does not set up the great passageway volume of recess part and can make the medium carry out quick water conservancy diversion, guarantees that the medium carries out quick, even distribution, does benefit to the medium and circulates more evenly in whole passageway, further improves heat transfer performance, guarantees permanent heat transfer stability.

In a particular embodiment, the width of the portion of the main panel 3 of the first panel 1 where the groove 321 is not provided is w1, and the width of the portion where the groove 321 is provided is w2, said w2 being 8-12 times the w 1. As shown in fig. 2, w1 is only the width of the non-grooved portion on one side, and is not the total width of all the non-grooved portions on one plate, the non-grooved portion can quickly guide and uniformly distribute the flowing medium, and the medium flows into the non-grooved portion again after completing heat exchange in the main heat exchange area with grooved portions in the middle, and uniformly gathers the medium together, and finally flows to the outlet, and the medium is uniformly distributed twice in the whole process, so that the medium can more uniformly and smoothly flow in the channel, the heat exchange performance can be improved, and the long-term heat exchange stability can be ensured.

In light of the foregoing, it will be apparent to those skilled in the art from this disclosure that various changes and modifications can be made without departing from the spirit and scope of the invention. The technical scope of the present invention is not limited to the content of the specification, and must be determined according to the scope of the claims.

Claims

1. A plate heat exchanger with asymmetric channels comprises a plurality of heat exchange plates which are stacked to form heat exchange channels, wherein the heat exchange plates are first plates (1) and second plates (2) which are alternately arranged, the first plates (1) and the second plates (2) respectively comprise a main panel (3) and surrounding baffle plates (4), a plurality of convex ridges (31) are arranged on the main panel (3), and valleys (32) are formed between the adjacent convex ridges (31), and the plate heat exchanger is characterized in that: a plurality of grooves (321) are uniformly distributed on the valley (32) of the first plate (1), so that asymmetric channels with different volumes are formed on two sides of the second plate (2).

2. A plate heat exchanger with asymmetric channels according to claim 1, wherein: the convex ridge (31) of the second plate (2) is clamped between two adjacent grooves (321) on the first plate (1), so that the top of the convex ridge (31) of the second plate (2) is contacted with the bottom of the valley (32) of the first plate (1), the upper ends of two sides of the convex ridge (31) of the second plate (2) are contacted with the side surfaces of the grooves (321) of the first plate (1), and welding points are formed at the contact parts.

3. A plate heat exchanger with asymmetric channels according to claim 1, wherein: the ridges (31) are arranged in a fishbone shape from the two axial sides of the first plate (1) or the second plate (2).

4. A plate heat exchanger with asymmetric channels according to claim 3, wherein: the second plate (2) is rotated 180 ° with respect to the first plate (1).

5. A plate heat exchanger with asymmetric channels according to claim 3, wherein: the valleys (32) of the first plate (1) are provided with grooves (321) at the middle axis position, and the rest grooves (321) are uniformly distributed from the grooves (321) at the middle axis position to two sides.

6. A plate heat exchanger with asymmetric channels according to claim 1, wherein: the height of the ridge (31) is 1.1 to 8 times the depth of the groove (321).

7. A plate heat exchanger with asymmetric channels according to claim 6, wherein: the height of the ridge (31) is 2-4 times of the depth of the groove (321).

8. A plate heat exchanger with asymmetric channels according to claim 1, wherein: four corners of the main panel (3) are provided with four corner holes (33), and grooves (321) are not arranged on part of valleys (32) of the first plate sheet (1) close to the corner holes (33).

9. A plate heat exchanger with asymmetric channels according to claim 8, wherein: the width of the part of the main panel (3) of the first sheet (1) where the groove (321) is not arranged is w1, the width of the part where the groove (321) is arranged is w2, and the w2 is 8-12 times of the w 1.