CN210802184U - Heat exchange plate - Google Patents

Abstract

The utility model relates to a heat exchange plate, which comprises a heat exchange area, a flanging and four end holes, wherein the heat exchange area comprises a plurality of continuous oblique flow areas along the longitudinal direction, any oblique flow area has a corrugated structure which extends obliquely and straightly relative to the longitudinal direction, and the corrugated extending directions of two adjacent oblique flow areas are different; the area of the output end hole extending towards the turned-over edge is an edge area, and the included angle between the corrugation of the edge area and the horizontal transverse line is larger than the included angle between the corrugation of the peripheral oblique flow area and the horizontal transverse line; the transition area between the input end hole and the main heat exchange area is a flow guide area, and the included angle between the ripple of the flow guide area and the horizontal transverse line is larger than the included angle between the ripple of the peripheral oblique flow area and the horizontal transverse line. The variable-angle pressure loss reduction design is adopted in the flow guide area around the input end hole and the edge area around the output end hole, and the heat exchange efficiency is further improved simultaneously for improving the uniformity that fluid, particularly condensing agent, flows from the input end hole to the main heat exchange area and flows from the main heat exchange area to the output end hole.

Description

Heat exchange plate

Technical Field

The utility model relates to a plate heat exchanger, concretely relates to heat transfer board with ripple structure.

Background

At present, a mature unpowered high-efficiency condenser specially suitable for the field does not appear in the market aiming at a top cooling system technology which does not consume energy by utilizing a heat pipe principle and is applied to cooling systems of data center base stations such as China Mobile, China telecom and 5G which are being constructed. The existing condenser belongs to a common heat exchanger because the condenser does not have the characteristics of high heat exchange efficiency, small volume, realization of unpowered driving due to fluorine side pressure drop and the like, and is matched with a cooling system in a large area and low efficiency.

The heat exchanger with higher heat exchange efficiency is developed, the size of the heat exchanger can be further reduced under the same heat exchange effect, and the development and market application of the unpowered condenser are facilitated. The use requirement of the condenser in the data center unpowered driving system of the current information base station is met.

Application publication No. CN102322763A discloses a plate heat exchanger plate with staggered corrugations, the heat exchange area of the plate has a corrugated structure, the longitudinal section corrugation heights of adjacent corrugated structures of the corrugated structure are different, and the longitudinal section corrugation heights of the corrugated structures separated by one corrugated structure are the same, so as to form a longitudinal high-low corrugated structure. The corrugated structure is in the shape of transverse straight corrugations, herringbone corrugations, straight corrugations, trapezoidal straight corrugations or zigzag corrugations in the fluid flowing direction. The pressure loss can be reduced by the design of high and low ripples.

Application publication number CN103727828A discloses a plate heat exchanger plate and a plate heat exchanger with unequal fluid channel cross-sectional areas, wherein a heat exchange area of the plate is a herringbone continuous corrugated area which enables the fluid channel cross-sectional areas on two sides of the plate heat exchanger plate to be unequal, the corrugation heights of the longitudinal sections of adjacent corrugated structures of the herringbone continuous corrugations are different, and the corrugation heights of the longitudinal sections of the corrugated structures separated by one corrugation are the same, so that a corrugated structure with continuous staggered longitudinal heights is formed, and the cross-sectional areas of the fluid channels on two sides of the plate are unequal. This patent application make full use of the access space that forms between plate heat exchanger slab, when the two sides flow of slab is unequal, the little medium of flow imports and exports the little one side of open area and flow through the little one side of passageway cross sectional area through plate heat exchanger medium, and the big medium of flow imports and exports the big one side of open area and flow through the big one side of passageway cross sectional area through plate heat exchanger medium to reduce the velocity of flow difference on two sides of slab, improved heat exchange efficiency, the cost is reduced.

In the plate heat exchanger, a circle of uniform welding points are generally distributed around a medium inlet at the inlet of two media, a bay is formed between adjacent welding points, and a heat exchange medium entering from the medium inlet can be retained by the bay, so that the heat exchange medium cannot smoothly enter a heat exchange flow channel between plate layers, and the heat exchange effect around the medium inlet is influenced.

The corrugated structure of the heat exchange area of the heat exchange plate is designed into the corrugated structure with staggered heights, which is beneficial to reducing pressure loss, but when in use, the low corrugated structure is easy to block between two adjacent welding points formed by the back surface of the low corrugated structure and the high corrugated structure of the adjacent heat exchange plate, thereby bringing ineffective pressure loss and reducing heat exchange efficiency.

In addition, for a plate heat exchanger, it is beneficial to improve the flow uniformity of the two media to improve the heat exchange efficiency, and taking a condenser as an example, it is ideal that the other heat exchange medium forms a loop around the gas phase inlet and the condensate outlet.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a heat exchange plate belongs to the heat transfer part of condenser, optimizes through the inlet end hole to the condensing agent and the flow direction trend around going out the liquid end hole, makes another medium form around inlet end hole and play liquid end hole and encircle, strengthens local heat exchange efficiency, promotes fluidic even flow.

The utility model provides a technical scheme that above-mentioned problem adopted does:

a heat exchange plate comprises a heat exchange area, a flanging and four end holes, wherein the flanging is positioned on the periphery of the heat exchange area, an input end hole and an output end hole which belong to the same medium in the four end holes are positioned on the same vertical side of the heat exchange area, the input end holes of a first heat exchange medium and the input end holes of a second heat exchange medium are arranged in opposite angles, the heat exchange plates are stacked, a heat exchange flow layer is formed between every two adjacent heat exchange plates, and the heat exchange flow layer of the first heat exchange medium and the heat exchange flow layer of the second heat exchange medium are spaced. The heat exchange area comprises a plurality of continuous oblique flow areas along the longitudinal direction, any oblique flow area has a straight corrugated structure which extends obliquely relative to the longitudinal direction, corrugations belonging to the same oblique flow area are parallel to each other, and the extending directions of the corrugations of two adjacent oblique flow areas are different, so that the first medium and the second medium generate baffling in the heat exchange area. The area of the output end hole extending towards the turned-over edge is an edge area, and the included angle between the corrugation of the edge area and the horizontal transverse line is larger than the included angle between the corrugation of the peripheral oblique flow area and the horizontal transverse line; the transition area between the input end hole and the main heat exchange area is a flow guide area, and the included angle between the ripple of the flow guide area and the horizontal transverse line is larger than the included angle between the ripple of the peripheral oblique flow area and the horizontal transverse line.

Preferably, the corrugated structures of the two diagonal flow areas welded together on the two adjacent heat exchange plates are mutually crossed, so that the heat exchange media on the two sides of the heat exchange plates form cross convection.

Preferably, the included angles between the corrugations of two adjacent oblique flow areas and the horizontal transverse line are equal but have different orientations, and the included angles between the corrugations of two oblique flow areas spaced by one oblique flow area and the horizontal transverse line are equal and have the same orientation, so that the first medium and the second medium are longitudinally and crossly baffled in the heat exchange area.

Compared with the prior art, the utility model has the characteristics of: in order to improve the uniformity of the fluid, especially the condensing agent, flowing from the input end hole to the main heat exchange area and flowing from the main heat exchange area to the output end hole, and further improve the heat exchange efficiency, the following variable-angle pressure loss reduction design is adopted in the local area:

at the feed position of the condensing agent: the hole of the input end of the condensing agent is close to the hole of the output end of the water, at the moment, the heat carried by the condensing agent is large, the transition area between the hole of the input end and the main heat exchange area is used as a flow guide area, and the included angle between the ripple of the flow guide area and the horizontal transverse line is reduced, so that the pressure loss of the water in the flow guide area is reduced, the water smoothly flows to the periphery of the hole of the input end of the condensing agent, the surrounding potential of the hole of the input end is formed, the heat exchange is enhanced, and meanwhile, the condensing agent can uniformly flow to the main heat exchange area.

At the refrigerant output position: the output end hole of condensing agent is close with the input end hole distance of water, and the temperature of water is lower this moment, regard the output end hole to the regional of the nearby extension of turn-ups around as the marginal zone, reduces the contained angle between the ripple and the horizontal transverse line of marginal zone to make another medium form in the marginal zone and encircle to the output end hole, strengthen the heat transfer.

Drawings

FIG. 1 is a front view of a condenser according to an embodiment of the present invention;

FIG. 2 is a side view of a condenser according to an embodiment of the present invention;

fig. 3 is a schematic structural view of a heat exchange plate a in the embodiment of the present invention;

fig. 4 is a schematic structural view of a heat exchange plate B in an embodiment of the present invention;

FIG. 5 is a partial schematic view of an edge region C1 of heat exchange panel A;

FIG. 6 is a partial schematic view of edge area C2 of heat exchange panel B;

FIG. 7 is a perspective view of a front-to-back stack of edge region C1 of heat exchange panel A and edge region C2 of heat exchange panel B;

FIG. 8 is a perspective view of the heat exchange areas of plate A and plate B stacked one on top of the other;

FIG. 9 is a schematic cross-sectional view of corrugations in a single heat exchanger plate;

FIG. 10 is a schematic view of a high corrugation without dimples and the back weld of an adjacent heat exchanger plate;

FIG. 11 is a schematic view of the high corrugation and the back side welding of adjacent heat exchange plates according to an embodiment of the present invention;

fig. 12 is a schematic structural view of an input end hole of a heat exchange plate a in the embodiment of the present invention;

fig. 13 is a schematic structural view of an input end hole of a heat exchange plate B in the embodiment of the present invention;

FIG. 14 is a perspective view of heat exchanger plate A superimposed one on top of the other with the inlet end holes of the heat exchanger plates;

fig. 15 is a schematic view of a conventional input port hole structure.

Number in the figure

1 front end plate

2 rear end plate

3 connecting pipe

4 reinforcing plate

5 heat exchange zone

6 zone of diagonal flow

7 high ripple

8 Low waviness

9 pits

10 welding point

11 arc-shaped corrugations radiating anticlockwise

11' arc-shaped corrugation radiating clockwise

12 input end hole peripheral welding point

13 bonding surface

14 "bay"

A1, A2, A3 and A4 are respectively a second medium output end hole, a second medium input end hole, a first medium output end hole and a first medium input end hole of the heat exchange plate A; b1, B2, B3 and B4 are respectively a second medium output end hole, a second medium input end hole, a first medium output end hole and a first medium input end hole of the heat exchange plate B; d1, D2, D3 and D4 are four connecting pipes respectively; c horizontal line.

Detailed Description

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

The utility model provides a condenser, is front end plate 1, a plurality of range upon range of heat transfer board, the back end plate 2 that welds each other together of range upon range of from the past backward in proper order, is provided with four takeover 3 on the front end plate, four end holes on the heat transfer board of butt joint respectively, set up in the cooperation department of takeover 3 and front end plate 1 and strengthen (fill up) board 4. Heat exchange flow layers for the circulation of a first medium (condensing agent in this embodiment) or a second medium (water in this embodiment) are formed between the front and the back adjacent heat exchange plates, and the heat exchange flow layers of the first medium and the heat exchange flow layers of the second medium alternate front and back. The stacked heat exchange plates are stacked in a manner that the heat exchange plates A and the heat exchange plates B are crossed.

The periphery of each heat exchange plate is turned over, the surface of each heat exchange plate is a heat exchange area, four end holes are arranged at four corners of the heat exchange area, the front end hole and the rear end hole of the series of heat exchange plates which correspond to each other are communicated, the input end hole and the output end hole which belong to the same medium in the four end holes are positioned on the same longitudinal side of the heat exchange area, and the input end holes of the first medium and the second medium are arranged in a diagonal manner.

As shown in the figure, the heat exchange zone 5 includes a plurality of continuous oblique flow zones 6 along the longitudinal direction, any oblique flow zone has a straight ripple structure extending obliquely relative to the longitudinal direction, ripples belonging to the same oblique flow zone are parallel to each other, the included angles between the ripples of two adjacent oblique flow zones 6 and the horizontal transverse line c are equal but different in direction, the included angles between the ripples of two oblique flow zones separated by one oblique flow zone and the horizontal transverse line c are equal and the same in direction, and the ripple structures of two oblique flow zones welded together in the front and at the back of two adjacent heat exchange plates are crossed with each other, so that the first medium and the second medium are deflected crosswise in the longitudinal direction of the heat exchange zone.

Furthermore, in the present embodiment, a shallow corrugation design is adopted to reduce the thermal resistance, and meanwhile, in order to reduce the resistance loss, full-height corrugations are adopted, as shown in fig. 9, the high corrugations and the low corrugations are arranged at intervals in a staggered manner, the heights H of the spaced high corrugations 7 are the same, and the heights H of the spaced low corrugations 8 are the same. As shown in the cross-sectional view of the corrugation, the corrugation height H of the high corrugation 7 is 1.8mm, the optimum corrugation height H of the low corrugation 8 adjacent to the high corrugation 7 is 0.9mm when the corrugation height H is 1/2H, and the distance L between two adjacent high corrugations 7 is 9.5mm, however, H may be H in any proportion (more than 0 and less than 1) in the implementation, and L may be defined according to the specification of the actual heat exchange plate. Due to the adoption of the high-low corrugation design, the high corrugations 7 on the front surface of the heat exchange plate at the back and the wave trough back surfaces of the adjacent heat exchange plates at the front form a joint point (welding point), as shown in fig. 10, because the corrugations on the heat exchange plates at the front and the back extend in a cross way and the wave trough intervals on two sides of the low corrugations 8 are often shorter, the flow channel blockage is easy to occur due to the too close distance between the adjacent two welding points 10 on the back surface of the low corrugations 8, and the problems of invalid pressure loss and partial heat exchange effect reduction are brought.

In order to solve the difficult problem that two adjacent solder joints at the back of low ripple 8 are too close and the runner is stifled, the utility model discloses adopt the breakpoint design in the middle of the closer solder joint of adjacent distance, increase the passageway between the ripple, let the fluid unblocked, form less bump in one side in addition simultaneously for the fluid is when flowing, mixes more evenly, promotes heat exchange efficiency greatly. Specifically be formed with sunken pit 9 between two welding points 10 on the wave surface of high ripple 7, pit 9 has enlarged the circulation hole between the double-phase nearly welding point, as shown in fig. 11, the sunken degree of depth of pit 9 is less than the ripple height of pit 9 place high ripple 7, at the back of high ripple 7, pit 9 just corresponds and forms the bump at adjacent heat transfer flow layer, this bump forms the vortex effect to the medium in the adjacent heat transfer flow layer, make the fluid when flowing, mix more evenly, promote heat exchange efficiency greatly.

The positions of the input end hole D4 of the first medium and the input end hole D2 of the second medium correspond to the orifices of the heat exchange plates A4, B4, A2 and B2, the input end hole usually has liquid inlet pressure, a circle of skirt is usually designed around the end hole for ensuring the strength of the end hole, the skirt is of a concave-convex structure, the front concave-convex structure and the rear concave-convex structure form a joint surface 13, waste of a heat exchange surface is caused, and a 'bay' 14 is formed between adjacent joint surfaces to enable fluid to be retained. As an improvement, the present invention adopts the design shown in fig. 12 and 13 in the input end hole, and involves arc-shaped ripples, circumferential: the corrugation is always a curve, and no wave crest or wave trough of a plane shape is generated; radial: the corrugations are radial, i.e. arc-shaped, and at the same time, the corrugation radiation directions of the two heat exchange plates are opposite, for example, the arc-shaped corrugations 11 of the heat exchange plate a radiate in the counterclockwise direction, and the arc-shaped corrugations 11' of the heat exchange plate B radiate in the clockwise direction, when the heat exchange plate a and the heat exchange plate B are laminated, the two arc-shaped corrugations form a joint point (welding point) at the inner ring of the ring where the arc-shaped corrugations are located, and the joint point is point contact. Both guaranteed that welding point 12 distributes evenly around the end hole, made the medium just begin the vortex when getting into the input end hole again, increased local heat transfer area, eliminated and detained "gulf" 14 of fluid, the distribution situation of reinforcing medium promotes heat exchange efficiency, has avoided the invalid pressure loss that the fluid is detained and has brought.

In order to improve the uniformity of the fluid, especially the condensing agent, flowing from the inlet port hole to the main heat exchange area and from the main heat exchange area to the outlet port hole, and further improve the heat exchange efficiency, the following variable-angle pressure loss reduction design is adopted in the local area.

At the feed position of the condensing agent: the distance between the hole of the input end of the condensing agent and the hole of the output end of the water is close, at the moment, the heat carried by the condensing agent is large, the transition area between the hole of the input end and the main heat exchange area is used as a flow guide area (E1, E2), and the included angle F between the ripple of the flow guide area (E1, E2) and the horizontal transverse line c is larger than the included angle between the ripple of the main heat exchange area and the horizontal transverse line c, so that the pressure loss of the water in the flow guide area (E1, E2) is reduced, the water smoothly flows to the periphery of the hole of the input end of the condensing agent, the surrounding potential of the hole of the input end is formed. And also facilitates the refrigerant in the flow guide areas (E1, E2) to flow uniformly to the main heat exchange area.

At the refrigerant output position: the distance between the output end hole of the condensing agent and the input end hole of the water is short, the temperature of the water is low at this time, the area, extending nearby, of the flanging of the output end hole to the periphery is used as an edge area (C1 and C2), the included angle F between the ripple of the edge area (C1 and C2) and the horizontal transverse line C is larger than the included angle between the ripple of the main heat exchange area and the horizontal transverse line C, and therefore the water tends to surround the output end hole of the condensing agent in the edge area (C1 and C2) to enhance heat exchange.

Although the preferred embodiments of the present invention have been described in detail hereinabove, it should be clearly understood that modifications and variations of the present invention are possible to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (3)

1. The utility model provides a heat exchange plate, includes heat transfer district, turn-ups, four end holes, the turn-ups is located heat transfer district edge all around, and the input end hole and the output end hole that belong to same medium in four end holes are located the vertical homonymy in heat transfer district, and the input end hole diagonal angle setting of first heat transfer medium and second heat transfer medium, and a plurality of heat exchange plate is range upon range of to form the heat transfer flow layer between two adjacent heat exchange plates, the heat transfer flow layer of first heat transfer medium and the heat transfer flow layer of second heat transfer medium are spaced each other its characterized in that:

the heat exchange area comprises a plurality of continuous oblique flow areas along the longitudinal direction, any oblique flow area has a straight corrugated structure which extends obliquely relative to the longitudinal direction, corrugations belonging to the same oblique flow area are parallel to each other, and the extending directions of the corrugations of two adjacent oblique flow areas are different, so that a first medium and a second medium generate baffling in the heat exchange area;

the area of the output end hole extending towards the turned-over edge is an edge area, and the included angle between the corrugation of the edge area and the horizontal transverse line is larger than the included angle between the corrugation of the peripheral oblique flow area and the horizontal transverse line;

the transition area between the input end hole and the main heat exchange area is a flow guide area, and the included angle between the ripple of the flow guide area and the horizontal transverse line is larger than the included angle between the ripple of the peripheral oblique flow area and the horizontal transverse line.

2. A heat exchanger plate according to claim 1, wherein: the corrugated structures of the two oblique flow areas welded together on the two adjacent heat exchange plates are mutually crossed.

3. A heat exchanger plate according to claim 1, wherein: the included angles between the ripples of two adjacent oblique flow areas and the horizontal transverse line are equal but have different orientations, and the included angles between the ripples of two oblique flow areas which are separated by one oblique flow area in the middle and the horizontal transverse line are equal and have the same orientation, so that the first medium and the second medium are longitudinally and crossly baffled in the heat exchange area.

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