CN210689333U

CN210689333U - Novel brazing heat exchange plate group

Info

Publication number: CN210689333U
Application number: CN201921863247.0U
Authority: CN
Inventors: 施吉璐; 韩维哲; 丁国良; 戚邗云
Original assignee: Weal Yield Jiangsu Heat Exchanger Co ltd
Current assignee: Weal Yield Jiangsu Heat Exchanger Co ltd
Priority date: 2019-10-31
Filing date: 2019-10-31
Publication date: 2020-06-05
Anticipated expiration: 2029-10-31

Abstract

The utility model belongs to the technical field of the brazing sheet formula heat exchanger slab, concretely relates to novel brazing heat exchanger slab group, including at least two pairs of unit slab groups, every first slab and the second slab of unit slab group including range upon range of setting, the second slab is 180 for first slab rotation, 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 valley, adjacent convex ridge's high difference between the convex ridge. The plate sheet of the heat exchange plate set is provided with a plurality of convex ridges on the main panel, concave valleys are formed between the adjacent convex ridges, the heights of the adjacent convex ridges are different, the height difference of the adjacent convex ridges can change the conventional turbulent flow generated when a medium flows in each single channel into an S-shaped turbulent flow, the overall turbulent flow degree of the heat exchanger is enhanced, the heat transfer coefficient of a single plate is improved, and the heat exchange efficiency is high; when the liquid filling amount is the same, the heat exchange area of the flow channel formed by the heat exchange plates is larger than the equal-height corrugated heat exchange plates.

Description

Novel brazing heat exchange plate group

Technical Field

The utility model belongs to the technical field of the plate heat exchanger that brazes, concretely relates to novel heat transfer board group of brazing.

Background

The core structural component of the brazed plate heat exchanger is a heat exchange plate with a certain corrugated shape, and the pattern design of each heat exchange plate determines the flowing state and the heat transfer effect of a medium in the heat exchanger, so that the heat exchange performance of the heat exchanger is directly determined. At present, brazed plate heat exchangers in the market are generally formed by combining high-grade pattern plates, the turbulence degree of media among the plates is low, heat exchange of cold and hot media is insufficient, and the heat transfer effect is poor. In order to strengthen the heat transfer effect, the number of the heat exchange plates is increased frequently, and the heat exchange area is increased, so that the realization of the average logarithmic temperature difference is ensured, the manufacturing process is increased, the manufacturing cost is raised, and the volume of the heat exchanger is greatly increased, so that more installation spaces need to be designed for the heat exchanger, the heat exchanger cannot be suitable for a machine set with a compact structure, and the development of light weight and miniaturization of mechanical equipment is not facilitated.

In addition, if the heat exchange area of the heat exchanger is small, in order to improve the heat exchange amount, a larger flow is needed, and the power of the circulating pump needs to be increased, so that the electric energy consumption is increased, and the energy waste is caused.

SUMMERY OF THE UTILITY MODEL

In order to solve the problem that the heat exchange efficiency of current brazing plate heat exchanger' S heat transfer slab is low, the utility model discloses a novel brazing heat transfer slab group, the slab of this slab group sets up a plurality of convex ridge on the main panel, form the valley between the adjacent convex ridge, and the high difference of adjacent convex ridge, the conventional torrent that the difference in height of adjacent convex ridge can make the medium produce when flowing in every single passageway becomes "S" shape torrent, the holistic torrent degree of heat exchanger is strengthened, the heat transfer has been reinforceed, the heat transfer coefficient of veneer has been improved, and the heat exchange efficiency is improved.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

the utility model provides a novel brazing heat exchange plate group, includes at least two pairs of unit plate groups, and is every right unit plate group is including first slab and the second slab of range upon range of setting, the second slab rotates 180 for first slab, 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, the high difference of adjacent convex ridge.

Preferably, the cross section of the ridge is an isosceles trapezoid.

Preferably, the ridges include a first ridge and a second ridge, the first ridge and the second ridge are alternately arranged, and the height a1 of the first ridge is greater than the height a2 of the second ridge.

Preferably, the height a1 of the first ridge is twice the height a2 of the second ridge.

Preferably, the length of the upper base of the first ridge of the isosceles trapezoid is b1, the length of the waist is c1, the distance between the vertical foot from the upper base top angle to the lower base and the vertical corner of the closer lower base is d1, the length of the upper base of the second ridge of the isosceles trapezoid is b2, the length of the waist is c2, the distance between the vertical foot from the upper base top angle to the lower base and the vertical corner of the closer lower base is d2, the length of the valley is b3, the length of the b1 is equal to b2 and is equal to b3, the length of the c1 is twice that of c2, and the length of the d1 is twice that of d 2.

Preferably, after the first plate and the second plate are assembled, the valley of the first plate is in contact with and aligned with the upper bottom of the first ridge of the second plate.

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

Preferably, the first plate and the second plate are both circular.

The utility model discloses following beneficial effect has: (1) the plate sheet of the heat exchange plate group of the utility model is provided with a plurality of convex ridges on the main panel, valleys are formed between the adjacent convex ridges, the heights of the adjacent convex ridges are different, the height difference of the adjacent convex ridges can change the conventional turbulence generated when a medium flows in each single channel into S-shaped turbulence, the overall turbulence degree of the heat exchanger is enhanced, the heat transfer is strengthened, the heat transfer coefficient of a single plate is improved, and the heat exchange efficiency is improved;

(2) under the condition that the liquid filling amount is the same, the heat exchange area of the runner of the heat exchanger formed by the heat exchange plate group is larger than the heat exchange area of the runner of the heat exchanger formed by the high-corrugation heat exchange plates commonly used at present, namely, the heat exchanger formed by the heat exchange plate group has larger heat exchange area and higher heat exchange efficiency, and under the condition that the obtained heat exchange amount is the same, the heat exchange plate group can adopt fewer heat exchange plates, is favorable for reducing the volume of the heat exchanger, can be suitable for a unit with compact structure, is favorable for the development of light weight and miniaturization of mechanical equipment, and is favorable for saving the manufacturing cost;

(3) the utility model discloses a runner that heat exchanger that heat transfer fin group constitutes formed has the big storehouse in the space great, the little storehouse in the space less and the runner of intercommunication big storehouse and little storehouse, the difference in height between big storehouse and the little storehouse can force the medium to gush into the little storehouse from the big storehouse, form "S" shape torrent, if under the unchangeable condition of heat transfer volume and heat transfer area, the torrent degree improves, the medium is imported and exported the difference in temperature and must be increased, then the medium flow can be reduced, the power of circulating pump just can be reduced, the energy that consumes under the condition that reaches the same heat transfer volume still less, the energy saving; for an air conditioning system, the reduction of the circulating amount and the using amount of the Freon means that the purchasing cost of the Freon is lower, and meanwhile, the air conditioning system is also beneficial to the protection of the atmosphere and the ozone layer;

(4) the improvement of the turbulence degree in the flow channel is also beneficial to reducing the scaling degree of the heat exchanger, so that the scaling period of the heat exchanger is prolonged, the cleaning times of the heat exchanger are reduced, and the workload and the maintenance cost of the heat exchanger are greatly reduced. Meanwhile, the cleaning frequency of the heat exchanger is reduced, so that the service life of the heat exchanger is prolonged.

Drawings

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

Fig. 1 is a schematic structural view of a heat exchange plate group of the present invention;

fig. 2 is a front view of the heat exchange plate of the present invention;

FIG. 3 is a cross-sectional view taken along line A-A of FIG. 2;

FIG. 4 is an enlarged view of a portion a of FIG. 3;

FIG. 5 is a schematic cross-sectional view of a flow path of a heat exchange plate pack;

FIG. 6 is a schematic cross-sectional view of a prior art heat exchanger plate having a contoured corrugation;

FIG. 7 is an enlarged view of portion b of FIG. 6;

in the figure: 1. a first sheet; 2. a second sheet; 31. a baffle plate; 41. a raised ridge; 411. a first convex ridge; 412. a second convex ridge; 42. a valley; 51. a channel; 52. a large bin; 53. and (5) small bins.

Detailed Description

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

A novel brazing heat exchange plate group is shown in figures 1-4 and comprises at least two pairs of unit plate groups, each pair of unit plate groups comprises a first plate 1 and a second plate 2 which are arranged in a stacked mode, the second plate 2 rotates 180 degrees relative to the first plate 1, the first plate 1 and the second plate 2 both comprise a main panel and surrounding baffle plates 31, a plurality of convex ridges 41 are arranged on the main panel, concave valleys 42 are formed between every two adjacent convex ridges 41, and the heights of the adjacent convex ridges 41 are different. As shown in fig. 5, the height difference between adjacent ridges 41 changes the conventional turbulence generated when the medium flows in each single channel into "S" shaped turbulence, so that the overall turbulence degree of the heat exchanger is enhanced, the heat transfer coefficient of the single plate is improved, and the heat exchange efficiency is improved.

In one particular embodiment, the cross-section of the ridge 41 is isosceles trapezoidal, as shown in fig. 3-4.

In a specific embodiment, as shown in fig. 3-4, ridge 41 comprises a first ridge 411 and a second ridge 412, wherein

ridges

411 and 412 are arranged alternately, and height a1 of ridge one 411 is greater than height a2 of ridge two 412.

In one specific embodiment, as shown in FIG. 4, the height a1 of ridge one 411 is twice the height a2 of ridge two 412.

In a specific embodiment, as shown in fig. 4, the length of the upper base of the first ridge 411 of the isosceles trapezoid is b1, the length of the waist is c1, the distance from the top corner of the upper base to the foot of the lower base to the closer top corner of the lower base is d1, the length of the upper base of the second ridge 412 of the isosceles trapezoid is b2, the length of the waist is c2, the distance from the top corner of the upper base to the foot of the lower base to the closer top corner of the lower base is d2, the length of the valley 42 is b3, b1 is equal to b2 is equal to b3, c1 is twice as long as c2, and d1 is twice as long as d 2.

As shown in fig. 6 to 7, the liquid filling amount of the flow channel formed by the conventional corrugated heat exchange plate is as follows:

V0 = 6×{ [(b4+2d1+b4)]×a1/2} = 6a1(b4+d1)

as shown in fig. 4, the liquid filling amount of the flow channel formed by the heat exchange plates of the present invention is:

V1 = 4×{[(b1+2d1+b1)]×a1/2}+4×{[(b2+2d2+b2)]×a2/2} +2×(a1-a2)×(b3+2d2+b2)

= 4a1(b1+d1) + 4a2(b2+d2) + 2×(a1-a2)×(b3+2d2+b2)

since a1=2a2, b1= b2= b3, d1=2d2,

V1 = 4a1(b1+d1) + 2a1(b1+0.5d1) + a1(2b1+d1)

= 4a1b1+4a1d1+2a1b1+a1d1+2a1b1+a1d1

= 8a1b1+6a1d1

= 6a1(4/3b1+d1)

as can be seen from fig. 4 and 7, the total length is L:

L=2b1+2b2+4b3+4d1+2d1=6b4+6d1

then: 8b1+6d1=6b4+6d1

d1=3/4b4

Namely: v0= V1

Therefore, the liquid filling amount of the flow channel formed by the heat exchange plates of the utility model is equal to that of the flow channel formed by the high-corrugation heat exchange plates commonly used at present.

As shown in fig. 7, the heat exchange area of the flow channel formed by the conventional corrugated heat exchange plate is as follows:

S0 = 6×(2c1+b4) = 12c1+6b4

as shown in fig. 4, the heat exchange area of the flow channel formed by the heat exchange plates of the present invention is:

S1 = 2×(4c1+2b1+2b2+2b3+4c2) = 12c1+12b1 = 12c1+9b4

namely: s1> S0

Therefore, the utility model discloses the heat transfer area of the runner that the heat transfer slab constitutes is greater than the heat transfer area of the runner that high ripple heat transfer slab constitutes of present commonly used. That is to say under the same condition of liquid charge volume, the utility model discloses a heat transfer slab has bigger heat transfer area, and heat exchange efficiency is higher, under the same condition of the heat transfer volume that obtains, the utility model discloses can adopt the heat transfer slab of still less quantity, be favorable to reducing the heat exchanger volume, practice thrift manufacturing cost.

In a specific embodiment, as shown in fig. 5, after the first plate 1 and the second plate 2 are assembled, the valley 42 of the first plate 1 contacts and aligns with the upper bottom of the first ridge 411 of the second plate 2. As shown in fig. 5, a narrow channel 51 is provided in the middle of the flow channel formed by the first plate 1 and the second plate 2, the left side and the right side of the channel 51 are respectively provided with a large bin 52 and a small bin 53 with large space, due to the existence of the channel 51 and the height difference between the large bin 52 and the small bin 53, when the medium in the flow channel flows from the large bin 52 into the small bin 53, an S-shaped turbulent flow is formed, the turbulent flow degree is increased, the heat transfer is enhanced, and the heat transfer coefficient K between the plates (or the heat transfer coefficient of the heat exchanger formed by combining the plates) is increased. If the turbulence degree is improved under the condition that the heat exchange quantity and the heat exchange area are not changed, the temperature difference between the medium inlet and the medium outlet is inevitably increased, the medium flow can be reduced, the power of the circulating pump can be reduced, less energy is consumed under the condition of reaching the same heat exchange quantity, and the energy is saved.

In addition, the improvement of the turbulence degree in the flow channel is also beneficial to reducing the scaling degree of the heat exchanger, so that the scaling period of the heat exchanger is prolonged, the cleaning times of the heat exchanger are reduced, and the workload and the maintenance cost of the heat exchanger are greatly reduced. Meanwhile, the service life of the heat exchanger is inevitably prolonged due to the reduction of the cleaning times of the heat exchanger.

In one embodiment, the ridges 41 are arranged in a fishbone pattern from the central axial side of the first or second panel 1, 2, as shown in fig. 1-2. In the embodiment, the ridges 41 may be arranged in a fishbone shape, and may be in various suitable shapes such as a wave shape and a twill shape.

In a particular embodiment, as shown in fig. 2, the first plate 1 and the second plate 2 are both circular. In the embodiment, the first plate 1 and the second plate 2 may have other suitable shapes such as a rectangular shape.

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. The utility model provides a novel brazing heat exchanger plate group which characterized in that: the laminated plate comprises at least two pairs of unit plate groups, each pair of unit plate groups comprises a first plate (1) and a second plate (2) which are arranged in a laminated mode, the second plate (2) rotates 180 degrees relative to the first plate (1), the first plate (1) and the second plate (2) comprise a main panel and surrounding baffles (31), a plurality of convex ridges (41) are arranged on the main panel, valley (42) are formed between every two adjacent convex ridges (41), and the heights of the adjacent convex ridges (41) are different.

2. The novel brazed heat exchanger plate pack of claim 1, wherein: the cross section of the convex ridge (41) is isosceles trapezoid.

3. The novel brazed heat exchanger plate pack of claim 2, wherein: the ridges (41) comprise a first ridge (411) and a second ridge (412), the first ridge (411) and the second ridge (412) are arranged alternately, and the height a1 of the first ridge (411) is greater than the height a2 of the second ridge (412).

4. The novel brazed heat exchanger plate pack of claim 3, wherein: the height a1 of ridge one (411) is twice the height a2 of ridge two (412).

5. The novel brazed heat exchanger plate pack of claim 4, wherein: the length of the upper bottom of a first convex ridge (411) of the isosceles trapezoid is b1, the length of the waist is c1, the distance from the upper bottom corner to the vertical foot of the lower bottom to the vertical corner of the closer lower bottom is d1, the length of the upper bottom of a second convex ridge (412) of the isosceles trapezoid is b2, the length of the waist is c2, the distance from the upper bottom corner to the vertical foot of the lower bottom to the vertical corner of the closer lower bottom is d2, the length of the valley (42) is b3, b1 is equal to b2 is equal to b3, c1 is twice as long as c2, and d1 is twice as long as d 2.

6. The novel brazed heat exchanger plate pack of claim 5, wherein: after the first plate (1) and the second plate (2) are assembled, the valley (42) of the first plate (1) is contacted and aligned with the upper bottom of the first ridge (411) of the second plate (2).

7. The novel brazed heat exchanger plate pack of claim 1, wherein: the ridges (41) are arranged in a fishbone shape from the two axial sides of the first plate (1) or the second plate (2).

8. The novel brazed heat exchanger plate pack of claim 1, wherein: the first plate (1) and the second plate (2) are both circular.