CN110749217A - A first plate for a multi-stage split brazing heat exchanger plate group - Google Patents

Abstract

The invention belongs to the technical field of heat exchangers, and in particular relates to a first plate for a multi-stage split-flow brazing heat exchanger plate group. The first plate includes a main panel and surrounding baffles. The main panel It includes a split area, a main heat exchange area and a confluence area, and between the split area and the main heat exchange area and between the main heat exchange area and the confluence area, there are diverting ribs, which are used to flow from the split area into the main heat exchange area. The medium from the main heat exchange area and the medium flowing into the confluence area are evenly distributed. In the present invention, the main panel of the heat exchange plate is provided with the diversion area, the main heat exchange area and the confluence area, and the diversion ribs are arranged between the diversion area and the main heat exchange area and between the main heat exchange area and the confluence area, which is beneficial to the medium. The uniform distribution of the heat exchanger is beneficial to improve the heat exchange performance and heat exchange stability of the heat exchanger.

Description

A first plate for a multi-stage split brazing heat exchanger plate group

technical field

The invention belongs to the technical field of heat exchangers, and in particular relates to a first plate for a multi-stage split flow brazing heat exchanger plate group.

Background technique

Brazed plate heat exchanger is a high-efficiency heat exchanger made of a series of metal sheets with a certain corrugated shape stacked and brazed. Channels are formed between various plates, and heat is exchanged through the plates. Compared with the conventional shell and tube heat exchanger, its heat transfer coefficient is much higher under the same flow resistance and pump power consumption, and it has a tendency to replace the shell and tube heat exchanger within the applicable range.

At present, in the design process of brazed plate heat exchangers on the market, most of them consider the fluidity of both ends of the heat exchanger without considering the fluidity of the medium near the middle of the plate. The medium circulation in the heat exchanger will change with the distance Longer, resulting in increased uneven flow, resulting in degraded or less stable heat exchanger performance.

SUMMARY OF THE INVENTION

In order to solve the problem that the medium circulation uniformity of the existing heat exchanger is poor, which leads to the performance of the heat exchanger being degraded or not stable enough, the invention discloses a multi-stage split-flow brazing heat exchanger plate set with a first plate, By arranging a diverter area, a main heat exchange area and a confluence area on the main panel of the first plate, and setting up diverter ribs between the diverter area and the main heat exchange area and between the main heat exchange area and the confluence area, it is beneficial to the Even distribution is beneficial to improve the heat exchange performance and heat exchange stability of the heat exchanger.

In order to achieve the above object, the present invention adopts the following technical solutions:

A first plate for a multi-stage split-flow brazed heat exchanger plate group, the first plate includes a main panel and surrounding baffles, the main panel includes a split area, a main heat exchange area and a confluence area , between the diverter area and the main heat exchange area and between the main heat exchange area and the confluence area are provided with diverter ribs, which are used for the medium flowing from the diverter area into the main heat exchange area and from the main heat exchange area into the confluence area. The medium is evenly distributed.

Preferably, the above-mentioned diverting area is provided with several convex ridges 1, a valley 1 is formed between adjacent convex ridges 1, and the included angle between the convex ridge 1 and the diverting ribs is α; the main heat exchange area is provided with Several convex ridges 2, two adjacent convex ridges form concave valleys 2, and the included angle between the convex ridges 2 and the diverting ribs is β; the confluence area is provided with several convex ridges 3, adjacent convex ridges A valley three is formed between the three, and the angle between the convex ridge three and the diverting rib is γ; the α is not equal to β; the β is not equal to γ.

Preferably, the first plate of the brazed heat exchanger plate group is used in the evaporator, the α is equal to γ, and is 30-45°, and β is 20-30°.

Preferably, the first plate of the brazed heat exchanger plate group is used for the condenser, the α is equal to γ, and is 20-30°, and β is 30-45°.

Preferably, the first ridges, the second ridges and the third ridges are inclined in the same direction; the heights of the first ridges, the second ridges and the third ridges are all equal and twice the height of the diverting ribs.

Preferably, a plurality of convex grooves protruding in the direction of the convex ridges are provided on the second valley of the first plate.

Preferably, the above-mentioned convex grooves are evenly distributed on the corresponding two valleys.

Preferably, the second ridge of the first plate has a ridge concave concave in the direction of the second valley along the top thereof, so as to increase the turbulent flow of the medium in the flow channel.

Preferably, the height of the above-mentioned convex ridge depression is equal to half of the height of the second convex ridge.

Preferably, the top of the second ridge of the first plate is divided into the first ridge 2 and the second ridge 2 by the ridge depression, the width of the top of the first ridge 2, the top of the second ridge 2 The width is equal to the width of the bottom of the valley 2 of the first plate, and is greater than the width of the bottom of the convex ridge and the concave.

A multi-stage split brazing heat exchanger plate group using the above-mentioned first plate, comprising at least two pairs of unit plate groups, each pair of the unit plate groups including a first plate and a second plate arranged in layers Plate, the second plate also includes a main panel and surrounding baffles.

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

Preferably, the second ridge of the second plate is provided with a plurality of grooves which are concave in the direction of the second valley.

Preferably, the above-mentioned convex grooves and grooves have the same size, and are evenly distributed on the corresponding second valleys and second ridges, respectively.

Preferably, the valley two of the second plate has a valley bulge protruding in the direction of the convex ridge two along the bottom thereof, so as to increase the turbulent flow of the medium in the flow channel.

Preferably, the heights of the above-mentioned ridge depressions and valley protrusions are equal.

Preferably, the bottom of valley 2 of the second plate is divided into first valley 2 and second valley 2 by the valley protrusions, the top width of the first ridge 2, the width of the second ridge 2 The top width, the bottom width of the second valley of the first plate, the bottom width of the first valley two, the bottom width of the second valley two and the top width of the second ridge of the second plate are all equal. The bottom width of the ridge depression is equal to the top width of the valley protrusion, and the top width of the second ridge is greater than the top width of the valley protrusion.

The present invention has the following beneficial effects:

(1) In the present invention, a diverter area, a main heat exchange area and a confluence area are set on the main panel of the first plate, and diverter ribs are set between the diverter area and the main heat exchange area and between the main heat exchange area and the confluence area The setting of the split ribs can make the medium flowing from the split area to the main heat exchange area to be evenly distributed at the split ribs, which is beneficial for the medium to flow into the main heat exchange area evenly. The distribution ribs between the hot area and the confluence area are distributed evenly, and they are evenly collected together, and flow through the confluence area to the outlet. Circulation, which is conducive to improving the formation of heat exchange and ensuring long-term heat exchange stability;

(2) The heat exchange plate of the present invention can be adjusted by adjusting the angle α between the ridge 1 and the diverting rib, the angle β between the ridge 2 and the diverting rib, and the angle between the ridge 3 and the diverting rib The size of γ is used to adjust the flow rate of the medium in three different areas, and by adjusting the size of β, the heat exchange plate is determined to be used in the evaporator or condenser;

(3) The heat exchange plate of the present invention is provided with convex grooves on the second valley and grooves on the second convex ridge. The setting of the convex grooves and the grooves is conducive to reducing the pressure drop in the flow channel, which is conducive to the improvement of the medium. Fast and uniform circulation to improve heat transfer performance;

(4) In the present invention, concave ridges and depressions are arranged at the top of the second ridges of the first plate, and convex valleys are arranged at the bottom of the second valleys of the second plate, so as to increase the medium in the flow channel. The turbulent flow is not only conducive to improving the heat exchange efficiency, but also can effectively avoid the accumulation of fouling and play a good antifouling effect.

Description of drawings

The present invention will be further described below in conjunction with the accompanying drawings and embodiments.

Fig. 1 is the structural representation of the heat exchange plate group of the present invention;

Fig. 2 is the structural representation of the first plate of the present invention;

Fig. 3 is an enlarged view of part a in Fig. 2;

Fig. 4 is an enlarged view of part b in Fig. 2;

Fig. 5 is the structural representation of the second plate of the present invention;

Fig. 6 is an enlarged view of part c in Fig. 5;

Fig. 7 is an enlarged view of part d in Fig. 5;

8 is a top view of a pair of unit plate groups of the present invention;

Fig. 9 is a sectional view along line A-A in Fig. 8;

Figure 10 is a cross-sectional view along line B-B in Figure 8;

In the figure: 1. The first plate; 2. The second plate; 3. The baffle plate; 41. The diversion area; 411. The ridge one; Two; 4211. The first ridge two; 4212. The second ridge two; 422. The valley two; 4221. The first valley two; 4222. The second valley two; 425. ridge depression; 426. valley protrusion; 43. confluence area; 431. ridge three; 432. valley three; 44. diverting ribs.

Detailed ways

The present invention will now be described in further detail with reference to the embodiments.

A first plate for a multi-stage split-flow brazed heat exchanger plate group, as shown in Figure 2, the first plate includes a main panel and surrounding baffles 3, the main panel includes a split area 41, a main heat exchange 42 and the confluence area 43, between the diversion area 41 and the main heat exchange area 42 and between the main heat exchange area 42 and the confluence area 43 are provided with diverting ribs 44, which are used to flow from the diversion area 41 into the main heat exchange area 42 The medium and the medium flowing into the confluence area 43 from the main heat exchange area 42 are evenly distributed. The arrangement of the diverting ribs 44 can make the medium flowing from the diverting area 41 to the main heat exchange area 42 evenly distributed at the diverting ribs 44, which is beneficial for the medium to flow into the main heat exchange area 42 evenly. , and then through the shunt rib 44 between the main heat exchange area 42 and the confluence area 43 for secondary distribution, uniformly collected together, and flowed to the outlet through the confluence area 43 . During the whole process, the medium is evenly distributed on both sides, which can make the medium circulate more evenly in the entire flow channel, which is beneficial to improve the heat exchange formation and ensure long-term heat exchange stability.

In addition, since the main panel of the heat exchange plate is provided with many corrugated ridges and valleys, which are prone to deformation, the arrangement of the diverting ribs 44 can provide effective support for the entire heat exchange plate, improve the strength of the panel, and is conducive to improving the Processing deformation problem.

In a specific embodiment, as shown in FIGS. 2-8 , the diversion area 41 is provided with several ridges 1 411 , a valley 1 412 is formed between adjacent ridge 1 411 , the ridge 1 411 and the diversion ribs are formed. The included angle between 44 is α; the main heat exchange area 42 is provided with several convex ridges 2 421, and valleys 2 422 are formed between the adjacent convex ridges 2 421, and the included angle between the convex ridges 2 421 and the diverting ribs 44 is β; the confluence area 43 is provided with a number of ridges 3 431, and valleys 3 432 are formed between adjacent ridges 3 431, and the angle between the ridges 3 431 and the diverting ribs 44 is γ; α is not equal to β; β is not equal to γ. If α is not equal to β, the medium will not flow directly from the diverter area 41 to the main heat exchange area 42, but will be distributed by the diverter ribs 44 before entering the main heat exchange area 42; if β is not equal to γ, the medium can also be passed through The distribution re-enters the sink area 43 .

In a specific embodiment, as shown in FIG. 8 , the first plate 1 for the brazed heat exchanger plate group is used for the evaporator, α is equal to γ, which is 30-45°, and β is 20-30° . Since evaporation is a process of converting liquid state into vapor state, setting the angle α (or γ) to a larger angle is more conducive to the rapid flow of liquid (or vapor state) into (or rapid evaporation out of) the main heat exchange area 42, thereby improving the Evaporation performance.

In a specific embodiment, as shown in FIG. 8 , the first plate 1 for the brazed heat exchanger plate group is used for the condenser, α is equal to γ, which is 20-30°, and β is 30-45° . Since condensation is a process of converting vapor state to liquid state, setting the α (or γ) angle to a larger angle is more conducive to the rapid inflow (or rapid outflow) of the vapor state (or liquid) into the main heat exchange area 42, thereby improving condensation performance.

In a specific embodiment, as shown in FIG. 9 and FIG. 10 , the first ridge 411, the second ridge 421 and the third ridge 431 are inclined in the same direction; the first ridge 411, the second ridge 421 and the The heights of the three 431 are all equal, and are equal to twice the height of the shunt rib 44 .

In a specific embodiment, as shown in FIGS. 3-4 , the second valley 422 of the first plate 1 is provided with a plurality of convex grooves 423 protruding toward the direction of the second ridge 421 . The convex grooves 423 provided on the second valley 422 are beneficial to reduce the pressure drop, facilitate the more rapid and uniform circulation of the medium, and improve the heat exchange performance.

In a specific implementation manner, as shown in FIG. 2 , the convex grooves 423 are evenly distributed on the corresponding valley two 422 .

In a specific embodiment, as shown in FIGS. 3-4 , the second ridge 421 of the first plate 1 has a ridge depression 425 concave in the direction of the second valley 422 along its top, which is convenient for increasing the medium in the flow channel. turbulence. As shown by the dotted line with arrows in Fig. 9, the medium can form turbulent flow in the flow channel, which is not only conducive to improving the heat exchange efficiency, but also can effectively avoid the accumulation of fouling, and play a good antifouling effect.

In a specific embodiment, as shown in FIG. 9 , the height of the ridge recess 425 is equal to half of the height of the second ridge 421 .

In a specific embodiment, as shown in FIGS. 3-4 and 9 , the top of the second ridge 421 of the first plate 1 is divided into a first ridge 2 4211 and a second ridge by the ridge depression 425 2 4212 , the top width of the first ridge 2 4211 , the top width of the second ridge 2 4212 and the bottom width of the valley 2 422 of the first plate 1 are all equal and larger than the bottom width of the ridge recess 425 .

A multi-stage split brazing heat exchanger plate group using the first plate, as shown in FIG. 1, includes at least two pairs of unit plate groups, and each pair of unit plate groups includes stacked first plates Sheet 1 and a second sheet 2, which also includes the main panel and surrounding baffles 3. Like the first plate 1 , the main panel of the second plate 2 also includes the above-mentioned diverting area 41 , the main heat exchange area 42 , the confluence area 43 and the diverting ribs 44 ; the diverting area 41 of the second plate 2 also has the same The plate 1 also includes the above-mentioned ridge-1 411 and valley-1 412, and the angle between the ridge-1 411 and the shunt rib 44 is also α; the main heat exchange area 42 of the second plate 2 is also connected to the first plate. Plate 1 also includes the above-mentioned ridges 2 421 and valleys 422, and the angle between the ridges 2 421 and the diverting ribs 44 is also β; the confluence area 43 of the second plate 2 is also the same as the first plate 1. Including the above-mentioned three convex ridges 431 and three concave valleys 432, the included angle between the three convex ridges 431 and the diverting ribs 44 is also γ.

In a specific embodiment, as shown in FIG. 1 , the second plate 2 is rotated 180° relative to the first plate 1 .

In a specific embodiment, as shown in FIGS. 6-7 , the second ridge 421 of the second plate 2 is provided with a plurality of grooves 424 recessed in the direction of the second valley 422 . The grooves 424 provided on the second ridge 421 are beneficial to reduce the pressure drop, facilitate the flow of the medium more quickly and evenly, and improve the heat exchange performance.

In a specific embodiment, as shown in FIG. 2 and FIG. 5 , the convex grooves 423 and the grooves 424 are equal in size and evenly distributed on the corresponding second valleys 422 and second ridges 421 respectively.

In a specific embodiment, as shown in FIGS. 6-7 , the second valley 422 of the second plate 2 has a valley protrusion 426 protruding toward the direction of the second ridge 421 along its bottom, which is convenient for increasing the medium Turbulence in the flow channel. As shown by the dotted line with arrows in Fig. 9, the medium can form turbulent flow in the flow channel, which is not only conducive to improving the heat exchange efficiency, but also can effectively avoid the accumulation of fouling, and play a good antifouling effect.

In a specific embodiment, as shown in FIGS. 9-10 , the heights of the ridge depressions 425 and the valley protrusions 426 are equal.

In a specific embodiment, as shown in FIGS. 3-4 , 6-7 and 9-10 , the bottom of the second valley 422 of the second plate 2 is divided into the first valley by the valley protrusion 426 . Valley 2 4221 and second valley 2 4222, the top width of the first ridge 2 4211, the top width of the second ridge 2 4212, the bottom width of the valley 2 422 of the first plate 1, the first valley 2 The bottom width of 4221, the bottom width of the second valley 2 4222 and the top width of the ridge 2 421 of the second plate 2 are all equal, and the bottom width of the ridge recess 425 is equal to the top width of the valley protrusion 426. The top width of the second ridge 4211 is larger than the top width of the valley protrusion 426 .

Taking the above ideal embodiments according to the present invention as inspiration, and through the above description, relevant personnel can make various changes and modifications without departing from the technical idea of the present invention. The technical scope of the present invention is not limited to the contents in the specification, and the technical scope must be determined according to the scope of the claims.

Claims (10)

1. A first plate for a multi-stage flow-splitting brazed heat exchanger plate package, the first plate (1) comprising a main panel and a surrounding baffle (3), characterized in that: the main panel comprises a flow distribution area (41), a main heat exchange area (42) and a confluence area (43), wherein flow distribution ribs (44) are arranged between the flow distribution area (41) and the main heat exchange area (42) and between the main heat exchange area (42) and the confluence area (43) and are used for uniformly distributing media flowing into the main heat exchange area (42) from the flow distribution area (41) and media flowing into the confluence area (43) from the main heat exchange area (42).

2. The first plate for the multi-stage flow division brazing heat exchanger plate group according to claim 1, wherein the flow division area (41) is provided with a plurality of first ridges (411), valley I (412) is formed between every two adjacent first ridges (411), the included angle between each first ridge (411) and the flow division rib (44) is α, the main heat exchange area (42) is provided with a plurality of second ridges (421), valley II (422) is formed between every two adjacent second ridges (421), the included angle between each second ridge (421) and the flow division rib (44) is β, the flow convergence area (43) is provided with a plurality of third ridges (431), valley III (432) is formed between every two adjacent third ridges (431), the included angle between each third ridge (431) and the flow division rib (44) is gamma, the α is not equal to β, and the β gamma is not equal to.

3. The first plate for a multi-split flow brazed heat exchanger plate pack according to claim 2, wherein the first plate (1) for a brazed heat exchanger plate pack is used for an evaporator, wherein α is equal to γ and is 30-45 ° and β is 20-30 °.

4. The first plate for a multi-split flow brazed heat exchanger plate pack as claimed in claim 2, wherein the first plate (1) for a brazed heat exchanger plate pack is used in a condenser, wherein α is equal to γ, and is 20-30 ° and β is 30-45 °.

5. A first plate for a multi-stage flow splitting brazed heat exchanger plate pack according to claim 2, characterized in that: the first ridge (411), the second ridge (421) and the third ridge (431) are inclined towards the same direction; the heights of the first ridge (411), the second ridge (421) and the third ridge (431) are all equal and equal to twice the height of the flow dividing rib (44).

6. A first plate for a multi-stage flow splitting brazed heat exchanger plate pack according to claim 2, characterized in that: and a plurality of convex grooves (423) protruding towards the direction of the second convex ridge (421) are arranged on the second concave valley (422) of the first plate (1).

7. The first plate for a multi-stage flow splitting brazed heat exchanger plate pack of claim 6, wherein: the convex grooves (423) are uniformly distributed on the corresponding second concave valleys (422).

8. A first plate for a multi-stage flow splitting brazed heat exchanger plate pack according to claim 2, characterized in that: the second ridge (421) of the first plate (1) is provided with a ridge recess (425) recessed towards the second valley (422) along the top of the second ridge, so that the turbulence of the medium in the flow channel is increased.

9. The first plate for a multi-stage flow splitting brazed heat exchanger plate pack of claim 8, wherein: the height of the ridge recess (425) is equal to half the height of the ridge two (421).

10. The first plate for a multi-stage flow splitting brazed heat exchanger plate pack of claim 8, wherein: the top of the second ridge (421) of the first plate (1) is divided into a second ridge (4211) and a second ridge (4212) by the ridge recess (425), and the top width of the second ridge (4211), the top width of the second ridge (4212) and the bottom width of the second valley (422) of the first plate (1) are all equal and larger than the bottom width of the ridge recess (425).

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