CN211626192U - Fluid heat exchanger - Google Patents

Abstract

The utility model discloses a fluid heat exchanger has solved the problem that the heat transfer rate of heat exchanger is low, and the technical scheme who solves this problem mainly includes a plurality of heat-conducting plates that stack layer upon layer, and front one side of heat-conducting plate is equipped with the circulation chamber that supplies liquid to flow, and the liquid in the adjacent circulation intracavity carries out the heat exchange through the heat-conducting plate, the heat-conducting plate is equipped with into water intercommunicating pore and play water intercommunicating pore, and the intercommunicating pore that intakes with play water intercommunicating pore all communicates with the circulation chamber of the front one side of heat-conducting plate, and the front of heat-conducting plate is equipped with the protruding muscle of vortex that is used for. The utility model discloses the protruding muscle of well vortex slows down the speed of rivers, prolongs the contact time of the liquid of unit volume and heat-conducting plate, has increased the positive area of contact of the liquid of circulation intracavity and heat-conducting plate for liquid and the positive heat transfer of heat-conducting plate.

Description

Fluid heat exchanger

Technical Field

The utility model relates to a small household electrical appliances technical field, especially a fluid heat exchanger.

Background

The working principle of the heat exchanger is that heat is transferred between fluids with different temperatures, and heat is transferred from the fluid with higher temperature to the fluid with lower temperature, so that the temperature of the fluid reaches a set temperature, energy is greatly saved, and the whole process is cleaner and more sanitary. The traditional heat exchanger mainly comprises a box body and a coil pipe arranged in the box body, wherein the two fluids with different temperatures flow inside and outside the coil pipe to exchange heat, but the coil pipe has large bending amplitude and large bending quantity and is inconvenient to process; meanwhile, the bent coil pipe occupies a large space, and the heat exchange rate of the heat exchanger is low, so that the traditional heat exchanger is not easy to be applied to household appliances with higher miniaturization and portability degrees. Therefore, it is a trend to develop a heat exchanger with a small size and a high heat exchange rate.

SUMMERY OF THE UTILITY MODEL

The utility model aims to reach the purpose be exactly provide a fluid heat exchanger, the protruding muscle of vortex slows down the speed of rivers, prolongs the contact time of the liquid of unit volume and heat-conducting plate, has increased the positive area of contact of the liquid of circulation intracavity and heat-conducting plate for liquid and the positive heat transfer of heat-conducting plate.

In order to achieve the above purpose, the utility model adopts the following technical scheme: the utility model provides a fluid heat exchanger, includes a plurality of heat-conducting plates that stack layer upon layer, and the front one side of heat-conducting plate is equipped with the circulation chamber that supplies liquid to flow, and the liquid in the adjacent circulation intracavity carries out the heat exchange through the heat-conducting plate, the heat-conducting plate is equipped with into water intercommunicating pore and play water intercommunicating pore, and the intercommunicating pore that intakes and go out water intercommunicating pore all communicate with the circulation chamber of the front one side of heat-conducting plate, and the front of heat-conducting plate is equipped with the protruding muscle of vortex that is used for.

Furthermore, the heat-conducting plate is provided with a turbulence groove on the back of the turbulence convex rib, and the projections of the turbulence convex rib and the turbulence groove in the same flow cavity on the longitudinal section of the heat-conducting plate are interwoven into a net shape.

Furthermore, the turbulence convex ribs are herringbone convex ribs, and the direction of the herringbone convex ribs is opposite to the direction of water flow in the circulation cavity; and/or the side surface of the turbulent convex rib is provided with a turbulent surface facing the water inlet communicating hole, and the included angle theta between the turbulent surface and the longitudinal section of the heat conducting plate is 100-125 degrees.

Furthermore, the protruding height h of the turbulent convex rib is 1 mm-1.3 mm; and/or a plurality of turbulence convex ribs are arranged in parallel, the protrusion height of each turbulence convex rib is h, the center distance between adjacent turbulence convex ribs is a, wherein h/a is more than or equal to 0.25 and less than or equal to 0.45; and/or the heat-conducting plate is a metal plate, the turbulent convex ribs are formed by punching the heat-conducting plate, and the thickness S of the heat-conducting plate is 0.3-0.5 mm.

Furthermore, the heat-conducting plate is provided with a first diversion rib between the water inlet communication hole and the turbulence convex rib for guiding water to uniformly flow to the turbulence convex rib, and the length direction of the first diversion rib is the same as the overall flowing direction of liquid in the circulation cavity.

Furthermore, the heat-conducting plate is equipped with the second water conservancy diversion muscle of guide liquid even flow direction first water conservancy diversion muscle in the outside of the intercommunicating pore of intaking, and the length direction of second water conservancy diversion muscle is the same with the radial of the intercommunicating pore of intaking.

Further, the edge of the front of the heat-conducting plate is provided with a reinforcing rib located on the outer side of the turbulence convex rib, an annular groove is formed in the front of the heat-conducting plate between the reinforcing rib and the turbulence convex rib, an annular sealing ring is arranged in the annular groove, and the adjacent heat-conducting plates are tightly clamped by the annular sealing ring to seal the circulation cavity.

Furthermore, the side face of the outer ring of the annular sealing ring is provided with a hanging buckle for limiting the annular sealing ring to move inwards, and the hanging buckle is abutted against the outer edge of the reinforcing rib for limiting.

Furthermore, the heat conducting plate is a rectangular plate, the water inlet communication hole and the water outlet communication hole are respectively arranged at two right angles of the heat conducting plate, and the water inlet communication hole and the water outlet communication hole are close to the same long edge or the same diagonal of the heat conducting plate; and/or, the heat-conducting plate is rectangular board, and the both ends of heat-conducting plate are located respectively to the intercommunicating pore of intaking and the intercommunicating pore of going out, and the aspect ratio of heat-conducting plate is 1/3 ~ 1/2.

Furthermore, four right-angle corners of the heat conducting plate are provided with round chamfers, and the arc edges of the round chamfers are intersected with the right-angle edges of the heat conducting plate.

After the technical scheme is adopted, the utility model has the advantages of as follows:

1. on one hand, the heat conducting plates are stacked layer upon layer, so that the occupied space of the heat conducting plates can be reduced, the miniaturization and the portability of the heat exchanger are facilitated, the flow path and time of liquid in the heat exchanger are increased, the heat exchange between the two kinds of liquid at the temperature is more sufficient, and the heat exchange effect of the heat exchanger is ensured; simultaneously, the circulation chamber is located the front one side of heat-conducting plate, and the area of contact of unit volume's liquid and heat-conducting plate is big, and heat exchange efficiency is high, has the liquid of different temperatures in the circulation chamber of heat-conducting plate both sides to the liquid that is located same circulation intracavity can carry out the heat exchange with the liquid of adjacent both sides circulation intracavity simultaneously, has further improved the heat exchange rate. On the other hand, the turbulence convex ribs block the flow of the liquid in the circulation cavity, slow down the speed of water flow and prolong the contact time between the liquid in unit volume and the heat-conducting plate, and the turbulence convex ribs also increase the surface area of the front surface of the heat-conducting plate, increase the contact area between the liquid in the circulation cavity and the front surface of the heat-conducting plate and accelerate the heat transfer between the liquid and the front surface of the heat-conducting plate; meanwhile, the turbulent flow convex ribs promote the liquid to be dispersed in the width direction of the heat guide plate, the liquid flows more uniformly in the flow cavity, and the heat exchange efficiency of the liquid at two temperatures is improved; in addition, the protruding muscle of vortex is located into between the intercommunicating pore and the water outlet intercommunicating pore to the protruding muscle of vortex is located the indispensable way of flowing through intracavity liquid flow, and the liquid of circulation intracavity can both pass through the disturbance of the protruding muscle of vortex promptly, guarantees the disturbance effect maximize of the protruding muscle of vortex, promotes the liquid of heat-conducting plate both sides to carry out the heat transfer.

2. The turbulent flow grooves increase the contact area between the liquid in the circulation cavity and the back surface of the adjacent heat-conducting plate, and accelerate the heat transfer between the liquid and the back surface of the adjacent heat-conducting plate; simultaneously, the liquid of the flow in the circulation intracavity receives the disturbance of vortex protruding rib and vortex recess simultaneously, and its disturbance effect to rivers is better, and the projection of vortex protruding rib and vortex recess on the longitudinal section of heat-conducting plate interweaves into netted to the direction of the rivers through the disturbance of vortex protruding rib and vortex recess is different, and the liquid disturbance is more even, and its heat transfer effect is better.

3. The direction of the herringbone convex ribs is opposite to the direction of water flow in the circulation cavity, so that liquid can be favorably dispersed and flowed towards the left side and the right side along the front surface of the heat conduction plate, namely, the liquid which just flows into the circulation cavity is dispersed in the width direction of the heat conduction plate due to the disturbance of the herringbone convex ribs, the liquid is promoted to uniformly flow along the front surface of the heat conduction plate, and the liquid heat exchange efficiency is improved.

The included angle theta between the turbulent flow surface and the longitudinal section of the heat conducting plate can be 100-125 degrees. When the included angle theta is larger than 125 degrees, the turbulent flow convex ribs are over flat, and the liquid can easily cross the free ends of the turbulent flow convex ribs under the action of self power, so that the liquid cannot uniformly and dispersedly flow in the width direction of the heat conducting plate, and the heat exchange efficiency of the liquid in unit volume is low; when the included angle theta is smaller than 100 degrees, the turbulent flow surface blocks the liquid from flowing forwards, the liquid capable of exchanging heat in the heat exchanger in unit time is limited, and particularly, the liquid is easy to gather at the root of the turbulent flow convex rib for a long time to cause reverse heat transfer.

4. The protruding height h of the turbulence convex rib is 1-1.3 mm, and the turbulence convex rib is beneficial to processing and forming under the condition that the heat exchanger has enough heat exchange efficiency. When the protruding height h of the turbulence convex rib is larger than 1.3mm, the occupied space of the whole heat conducting plate in the thickness direction is too large, the miniaturization and the portability of the heat exchanger are not facilitated, and the molding of the turbulence rib is inconvenient; when the protruding height h is less than 1mm, the flow disturbing effect of the whole flow disturbing convex rib is poor, and the heat exchange efficiency is low.

The ratio h/a of the height of the turbulent convex ribs to the center distance is 0.25 to 0.45. When h/a is more than 0.45, the heat conducting plate can generate limited stamping deformation, so that the heat conducting plate is easy to damage in the stamping process; when h/a is less than 0.25, the distribution density of the turbulence convex ribs on the front surface of the heat conducting plate is too small, and the turbulence effect is limited.

The thickness S of the heat conducting plate made of the metal material is 0.3 mm-0.5 mm, so that the machining and forming of the turbulence convex ribs are facilitated, and the heat transfer efficiency of liquid is ensured. When the thickness of the heat conducting plate is less than 0.3mm, the thickness of the heat conducting plate is thin, the turbulent flow convex ribs on the heat conducting plate are difficult to form, the strength of the heat conducting plate is low, and the heat conducting plate is easy to deform to cause water leakage when being impacted by liquid with high pressure; when the thickness of the heat conducting plate is larger than 0.5mm, the heat resistance of the heat conducting plate is larger, and the heat transfer efficiency of the liquid at the two sides of the heat conducting plate is low.

5. The length direction of first water conservancy diversion muscle is the same with the direction of circulation intracavity rivers to the liquid that just flows into the circulation chamber can evenly flow to the protruding muscle of vortex under the drainage effect of first water conservancy diversion muscle, promotes promptly that the liquid that flows into the circulation intracavity can disperse on the width direction of heat-conducting plate fast, and liquid and the positive abundant contact of heat-conducting plate improve heat exchange efficiency.

Drawings

The present invention will be further explained with reference to the accompanying drawings:

fig. 1 is a structural view of a fluid heat exchanger according to a first embodiment of the present invention;

FIG. 2 is an exploded view of a fluid heat exchanger according to one embodiment of the present invention;

FIG. 3 is a structural diagram of a first layer of heat-conducting plate with a ring-shaped sealing ring installed thereon according to the first embodiment;

FIG. 4 is a longitudinal partial sectional view of a thermal plate according to one embodiment of the present invention;

FIG. 5 is a structural diagram of a heat-conducting plate according to one embodiment of the present invention;

FIG. 6 is a partial enlarged view of a heat conducting plate according to one embodiment;

FIG. 7 is a partial enlarged view of the heat conductive plate of the first embodiment;

FIG. 8 is a front view of the o-ring seal on the first layer of the plate in accordance with one embodiment;

fig. 9 is a front view of the o-ring on the first plate of the second embodiment.

Detailed Description

The utility model discloses in, the heat-conducting plate has two sides, and arbitrary one side all can be the front of heat-conducting plate in two sides of heat-conducting plate, so, another side is the back of heat-conducting plate on the heat-conducting plate, but the front orientation of all heat-conducting plates that stack is the same, and is the same for the back orientation of all heat-conducting plates that stack.

Example one

As shown in fig. 1 to 3, the present embodiment provides a fluid heat exchanger, including upper bracket 1, lower bracket 2 and heat conducting plate 3, heat conducting plate 3 is equipped with a plurality of and layer upon layer and puts between upper bracket 1 and lower bracket 2, and front one side of heat conducting plate 3 is equipped with the circulation chamber that supplies liquid to flow, and the liquid in the adjacent circulation chamber carries out the heat exchange through heat conducting plate 3, heat conducting plate 3 is equipped with into water intercommunicating pore 311 and play water intercommunicating pore 312, and into water intercommunicating pore 311 and play water intercommunicating pore 312 all communicate with the circulation chamber of front one side of heat conducting plate 3, and the front of heat conducting plate 3 is equipped with the vortex projecting rib 30 that is used for accelerating heat exchange speed, and vortex projecting rib 30 is located between.

On one hand, the heat conducting plates 3 are stacked layer by layer, so that the occupied space of the heat conducting plates 3 can be reduced, the miniaturization and the portability of the heat exchanger are facilitated, the flow path and time of liquid in the heat exchanger are increased, the heat exchange between the two kinds of liquid at the temperature is more sufficient, and the heat exchange effect of the heat exchanger is ensured; meanwhile, the circulation cavity is positioned on one side of the front surface of the heat conducting plate 3, the contact area of liquid in unit volume and the heat conducting plate 3 is large, the heat exchange efficiency is high, and liquid with different temperatures is arranged in the circulation cavities on two sides of the heat conducting plate 3, so that the liquid in the same circulation cavity can exchange heat with the liquid in the circulation cavities on two adjacent sides simultaneously, and the heat exchange rate is further improved. On the other hand, the turbulence convex ribs 30 obstruct the flow of the liquid in the circulation cavity, slow down the speed of water flow, and prolong the contact time between the liquid in unit volume and the heat-conducting plate 3, and the turbulence convex ribs 30 also increase the surface area of the front surface of the heat-conducting plate 3, increase the contact area between the liquid in the circulation cavity and the front surface of the heat-conducting plate 3, and accelerate the heat transfer between the liquid and the front surface of the heat-conducting plate 3; meanwhile, the turbulent flow convex ribs 30 promote the liquid to be dispersed in the width direction of the heat guide plate 3, the liquid flows more uniformly in the flow cavity, and the heat exchange efficiency of the liquid with two temperatures is improved; in addition, the protruding muscle 30 of vortex is located into between the intercommunicating pore 311 and the intercommunicating pore 312 that gives water to the protruding muscle 30 of vortex is located the indispensable way of flowing of circulation intracavity liquid, and the liquid in the circulation intracavity can both pass through the disturbance of the protruding muscle 30 of vortex promptly, guarantees the disturbance effect maximize of the protruding muscle 30 of vortex, promotes the liquid at heat-conducting plate 3 both sides to carry out the heat transfer.

With reference to fig. 4, the heat conducting plate 3 is provided with a turbulent flow groove 34 on the back of the turbulent flow rib 30, and the turbulent flow rib 30 and the turbulent flow groove 34 in the same flow cavity are interlaced to form a mesh shape in the projection on the longitudinal section of the heat conducting plate 3. The turbulent flow grooves 34 increase the contact area between the liquid in the circulation cavity and the back surface of the adjacent heat-conducting plate 3, and accelerate the heat transfer between the liquid and the back surface of the adjacent heat-conducting plate 3; meanwhile, the flowing liquid in the circulation cavity is disturbed by the turbulence convex ribs 30 and the turbulence grooves 34, the disturbing effect of the liquid on the water flow is better, the projections of the turbulence convex ribs 30 and the turbulence grooves 34 on the longitudinal section of the heat-conducting plate 3 are interwoven into a net shape, so that the direction of the water flow disturbed by the turbulence convex ribs 30 and the turbulence grooves 34 is different, the liquid disturbance is more uniform, and the heat exchange effect is better.

Combine fig. 5 and fig. 6, the protruding muscle of vortex 30 is the protruding muscle of chevron shape, and the direction of the protruding muscle of chevron shape is opposite with the direction of circulation intracavity rivers, does benefit to liquid along heat-conducting plate 3 openly to left and right sides dispersion flow, and the liquid that just flows into the circulation intracavity promptly is owing to receive the disturbance of the protruding muscle of chevron shape and the width direction dispersion of heat-conducting plate 3, promotes liquid along the positive uniform flow of heat-conducting plate 3, improves liquid heat exchange efficiency. In the embodiment, the included angle alpha of the herringbone convex ribs is preferably 115-125 degrees, so that the liquid has certain flowing speed in the length direction and the width direction of the heat conducting plate 3, the liquid can be guided to be rapidly dispersed in the width direction of the heat conducting plate 3, and the phenomenon that the liquid flows too slowly in the flowing cavity to generate reverse heat exchange is avoided; of course, the included angle α of the herringbone ribs may also be an acute angle or a right angle, for example, α may be 30 °, 45 °, 60 °, 75 °, or 90 °. It is understood that the turbulence ribs 30 may be long ribs, and the length direction of the long ribs is the same as the width or length direction of the heat-conducting plate 3.

In this embodiment, the side surface of the turbulent protruding rib 30 is provided with a turbulent surface 301 facing the water inlet communication hole 311, and in order to ensure the overall heat exchange efficiency of the heat exchanger, an included angle θ between the turbulent surface 301 and the longitudinal section of the heat conducting plate 3 may be 100-125 °. When the included angle theta is larger than 125 degrees, the turbulent flow convex ribs 30 are too flat, and the liquid can easily cross the top ends of the turbulent flow convex ribs 30 under the action of the self power, so that the liquid cannot uniformly and dispersedly flow in the width direction of the heat conduction plate 3, and the heat exchange efficiency of the liquid in unit volume is low; when the included angle θ is smaller than 100 °, the turbulent flow surface 301 blocks the liquid from flowing forward, the liquid that can be exchanged by the heat exchanger in unit time is limited, and particularly, the liquid is easily gathered at the root of the turbulent flow convex rib 30 for a long time to cause reverse heat transfer.

In this embodiment, under the condition that the heat exchanger has a sufficiently large heat exchange efficiency, the protruding height h of the turbulent convex rib 30 may be 1mm to 1.3mm in order to facilitate the processing and molding of the turbulent convex rib 30. When the protruding height h of the turbulent flow convex rib 30 is larger than 1.3mm, the occupied space of the whole heat conducting plate 3 in the thickness direction is too large, the miniaturization and the portability of the heat exchanger are not facilitated, and the turbulent flow convex rib 30 is inconvenient to form, particularly, the heat conducting plate 3 in the embodiment is a metal plate with better heat conductivity, the turbulent flow convex rib 30 is formed by punching the heat conducting plate 3, when the protruding height h is larger than 1.3mm, the punching breakage rate is high, even if the complete turbulent flow convex rib 30 is formed by punching, the turbulent flow convex rib 30 is easy to be broken under the impact of liquid due to the thinner wall thickness of the turbulent flow convex rib 30; when the protruding height h is less than 1mm, the whole turbulent convex rib 30 has poor turbulent effect and low heat exchange efficiency.

In this embodiment, the spoiler ribs 30 are provided in a plurality and arranged in parallel, and the center distance between adjacent spoiler ribs 30 is a, wherein h/a is greater than or equal to 0.25 and less than or equal to 0.45; when h/a is more than 0.45, the heat conducting plate 3 can generate limited stamping deformation, so that the heat conducting plate is easy to damage in the stamping process; when h/a is less than 0.25, the distribution density of the turbulent flow convex ribs 30 on the front surface of the heat conducting plate 3 is too small, and the turbulent flow effect is limited.

In this embodiment, the thickness S of the heat conducting plate 3 made of metal is 0.3mm to 0.5mm, which not only facilitates the processing and forming of the turbulence ribs 30, but also ensures the heat transfer efficiency of the liquid. When the thickness of the heat conducting plate 3 is less than 0.3mm, the thickness of the heat conducting plate 3 is thinner, the turbulent convex ribs 30 on the heat conducting plate 3 are difficult to form, the strength of the heat conducting plate 3 is low, and the heat conducting plate 3 is easy to deform to cause water leakage when being impacted by liquid with higher pressure; when the thickness of the heat conducting plate 3 is larger than 0.5mm, the heat resistance of the heat conducting plate 3 is larger, and the heat transfer efficiency of the liquid at the two sides of the heat conducting plate 3 is low.

In order to promote the liquid flowing into the circulation cavity to disperse in the width direction of the heat conducting plate 3, the heat conducting plate 3 is provided with a first diversion rib 351 for guiding the water to flow to the turbulence convex rib 30 to flow uniformly between the water inlet communication hole 311 and the turbulence convex rib 30, and the length direction of the first diversion rib 351 is the same as the whole flowing direction of the liquid in the circulation cavity. In this embodiment, first water conservancy diversion muscle 351 is equipped with a plurality ofly and distributes side by side along the width direction of heat-conducting plate 3, and at this moment, the liquid that just flows into the circulation chamber can evenly flow to the protruding muscle 30 of vortex under the drainage effect of the first water conservancy diversion muscle 351 that distributes side by side, and liquid and the positive abundant contact of heat-conducting plate 3 improve heat exchange efficiency.

Similarly, referring to fig. 7, in order to promote the liquid flowing into the flow chamber to uniformly flow to the first flow guiding rib 351, the heat conducting plate 3 may be provided with a second flow guiding rib 352 outside the water inlet communication hole 311 for guiding the liquid to uniformly flow to the first flow guiding rib 351, and the length direction of the second flow guiding rib 352 is the same as the radial direction of the water inlet communication hole 311. Therefore, the liquid which just flows into the flow cavity flows outwards and diverges under the action of the second flow guide ribs 352, so that the liquid which is distributed side by side and has enough amount flows into the upstream of the first flow guide ribs 351, and then flows uniformly to the turbulence convex ribs 30 under the shunting action of the first flow guide ribs 351.

For improving the intensity at the edge of heat-conducting plate 3, avoid the protruding muscle 30 punching press of vortex to form back heat-conducting plate 3 marginal emergence deformation, the positive edge of heat-conducting plate 3 can be equipped with the strengthening rib 36 that is located the protruding muscle 30 outsides of vortex, and simultaneously, the front of heat-conducting plate 3 is equipped with annular groove 33 between strengthening rib 36 and the protruding muscle 30 of vortex, is equipped with ring packing 5 in the annular groove 33, and adjacent heat-conducting plate 3 presss from both sides tight ring packing 5 and will circulate the chamber and seal. The reinforcing ribs 36 and the turbulence reinforcing ribs 30 which are protruded from the front surface of the heat conducting plate 3 are clamped to form the annular groove 33, so that the structure of the heat conducting plate 3 is simplified, and the phenomenon that the strength of the heat conducting plate 3 is reduced due to independent slotting is avoided; meanwhile, the annular sealing ring 5 with good elasticity realizes the sealing of the circulation cavity, so that liquid is prevented from leaking from the edge of the heat conducting plate 3, the deformation of the annular sealing ring 5 in the axial direction and the radial direction is large, the thermal expansion and the cold contraction of the circulation cavity on two sides of the heat conducting plate 3 are facilitated, and the sealing effect of the annular sealing ring 5 on the circulation cavity is further ensured.

With reference to fig. 8, in order to facilitate the stacking and installation of the heat conducting plates 3, the outer ring side surface of the annular sealing ring 5 may be provided with a hanging buckle 53 for limiting the inward movement of the annular sealing ring 5, and the hanging buckle 53 abuts against and is limited by the outer edge of the reinforcing rib 36. Therefore, when the annular sealing ring 5 is tightly pressed by the adjacent heat conduction plate 3, the annular sealing ring 5 can still be reliably arranged in the annular groove 33, and the sealing effect of the annular sealing ring 5 on the circulation cavity is ensured.

In this embodiment, the heat conducting plate 3 is a rectangular plate, the water inlet communication hole 311 and the water outlet communication hole 312 are respectively disposed at two ends of the heat conducting plate 3, and the width-to-height ratio X of the heat conducting plate 3 is 1/3-1/2. When the width-to-height ratio X of the heat conducting plate 3 is greater than 1/2, the width of the heat conducting plate 3 is too large, the flow distribution on the left and right sides of the heat conducting plate 3 is uneven, and even the liquid at the local edge position cannot reach; when the width-to-height ratio X is smaller than 1/3, the length of the heat conducting plate 3 is too long, and the occupied space of the heat exchanger is large. Meanwhile, in order to reduce the defective rate of the die stamping of the heat conducting plate 3, four right-angle corners of the heat conducting plate 3 are provided with round chamfers, and the circular edges 37 of the round chamfers are intersected with the right-angle edges 38 of the heat conducting plate 3. Thereby reducing the precision requirement of die stamping forming, improving the yield and reducing the die strain.

In this embodiment, the heat-conducting plate 3 is further provided with a water inlet blocking hole 321 and a water outlet blocking hole 322 located inside the annular sealing ring 5, and it can be understood that the water inlet communication hole 311 is communicated with the water inlet blocking hole 321 of the adjacent heat-conducting plate 3, the water outlet communication hole 312 is communicated with the water outlet blocking hole 322 of the adjacent heat-conducting plate 3, the water inlet blocking hole 321 is communicated with the water inlet communication hole 311 of the adjacent heat-conducting plate 3, and the water outlet blocking hole 322 is communicated with the water outlet communication hole 312 of the adjacent heat-conducting plate 3. Therefore, the liquid flowing out from the water inlet partition hole 321 of the previous heat-conducting plate 3 can partially exchange heat through the circulation cavity on one side of the front surface of the current heat-conducting plate 3 and then flow out from the water outlet communication hole 312, and the other part flows to the water inlet partition hole 321 of the next heat-conducting plate 3 through the water inlet communication hole 311 of the current heat-conducting plate 3, so that the liquid after heat exchange is ensured to be discharged in time, the reverse heat exchange caused by continuous flow is avoided, the liquid flowing and updating rate is also improved, and the heat exchange efficiency of the heat exchanger is ensured.

Specifically, the water inlet intercommunicating pore 311, the water outlet intercommunicating pore 312, the water inlet partition hole 321 and the water outlet partition hole 322 on the same heat conducting plate 3 are respectively arranged on four right angles of the heat conducting plate 3, the water inlet intercommunicating pore 311 and the water outlet intercommunicating pore 312 are close to the same long edge of the heat conducting plate 3, the contact length of the liquid with the heat conducting plate 3 in the circulation cavity is ensured to be large enough, the heat exchange of the liquid in the adjacent circulation cavities is more sufficient, simultaneously, the shape and the structure of the heat conducting plate 3 are symmetrical, the heat conducting plate 3 provided with the ring-shaped sealing ring 5 only needs to rotate 180 degrees to form the heat conducting plate 3 provided with the ring-shaped sealing ring 5 in the. In addition, in order to ensure that the water inlet communication hole 311 and the water outlet communication hole 312 are both communicated with the circulation cavity on the front side of the heat conducting plate 3, in the embodiment, the annular sealing ring 5 is respectively provided with a water inlet opening 511 and a water outlet opening 512 outside the water inlet communication hole 311 and the water outlet communication hole 312, the water inlet communication hole 311 is communicated with the circulation cavity on the front side of the heat conducting plate 3 through the water inlet opening 511, and the water outlet communication hole 312 is communicated with the circulation cavity on the front side of the heat conducting plate 3 through the water outlet opening 512.

Correspondingly, the water inlet partition hole 321 and the water outlet partition hole 322 are close to the other long edge of the heat conducting plate 3, and are mainly separated from the circulation cavity on one side of the front surface of the heat conducting plate 3 through the annular sealing ring 5, specifically, the annular sealing ring 5 is in axial symmetry, the annular sealing ring 5 is provided with a water inlet blocking rib 521 for separating the water inlet partition hole 321 from the circulation cavity on one side of the front surface of the heat conducting plate 3, the annular sealing ring 5 is further provided with a water outlet blocking rib 522 for separating the water outlet partition hole 322 from the circulation cavity on one side of the front surface of the heat conducting plate 3, and the water inlet blocking rib 521 and the water outlet blocking rib 522 are close to the same long edge of the annular.

In this embodiment, the upper rack 1 and the lower rack 2 are rectangular structures, the upper rack 1 is provided with a first water inlet a1, a first water outlet B1, a second water inlet a2 and a second water outlet B2, the first water inlet a1 is communicated with the water inlet communication hole 311 of the heat conducting plate 3 adjacent to the upper rack 1, the first water outlet B1 is communicated with the water outlet communication hole 312 of the heat conducting plate 3 adjacent to the upper rack 1, correspondingly, the second water inlet a2 is communicated with the water inlet blocking hole 321 of the heat conducting plate 3 adjacent to the upper rack 1, and the second water outlet B2 is communicated with the water outlet blocking hole 322 of the heat conducting plate 3 adjacent to the upper rack 1.

In this embodiment, four heat conduction plates 3 are provided, and from the upper bracket 1, a first heat conduction plate, a second heat conduction plate, a third heat conduction plate and a fourth heat conduction plate are sequentially provided, wherein the first heat conduction plate and the third heat conduction plate have the same structural shape, and the second heat conduction plate and the fourth heat conduction plate have the same structural shape, which mainly means that the positions of the water inlet communication hole 311, the water outlet communication hole 312, the water inlet partition hole 321 and the water outlet partition hole 322 on the heat conduction plate 3 are the same, wherein the second heat conduction plate can be obtained by rotating the first heat conduction plate by 180 degrees.

In this embodiment, the front surface of the heat conducting plate 3 means that the side surface of the heat conducting plate 3 facing the upper bracket 1 is the front surface, and correspondingly, the side surface of the heat conducting plate 3 facing away from the upper bracket 1 is the back surface. Of course, the front surface of the heat conducting plate 3 may also be the side surface of the heat conducting plate 3 departing from the upper bracket 1, and correspondingly, the side surface of the heat conducting plate 3 facing the upper bracket 1 is the back surface of the heat conducting plate 3.

Example two

As shown in fig. 9, it is understood that the heat conducting plate 3 is a rectangular plate, and the water inlet communication hole 311 and the water outlet communication hole 312 may be close to the same diagonal line of the heat conducting plate 3. At this time, the distance of the liquid flowing in the circulation chamber is longer, and the liquid flows uniformly in the width direction of the heat conduction plate 3, so that the heat exchange efficiency of the adjacent circulation chambers is higher.

Correspondingly, the inlet partition hole 321 and the outlet partition hole 322 are also close to the other diagonal of the heat conducting plate 3, which is mainly isolated from the circulation chamber on the front side of the heat conducting plate 3 by the ring seal 5. Specifically, the annular sealing ring 5 is centrosymmetric, the annular sealing ring 5 is provided with a water inlet blocking rib 521 for blocking the water inlet blocking hole 321 from the circulation cavity on one side of the front surface of the heat conducting plate 3, the annular sealing ring 5 is also provided with a water outlet blocking rib 522 for blocking the water outlet blocking hole 322 from the circulation cavity on one side of the front surface of the heat conducting plate 3, and the water inlet blocking rib 521 and the water outlet blocking rib 522 are respectively close to two opposite angles of the annular sealing ring 5; correspondingly, the annular sealing ring 5 is provided with a water inlet opening 511 and a water outlet opening 512 respectively outside the water inlet communication hole 311 and the water outlet communication hole 312, the water inlet communication hole 311 is communicated with the circulation cavity on the front side of the heat conducting plate 3 through the water inlet opening 511, the water outlet communication hole 312 is communicated with the circulation cavity on the front side of the heat conducting plate 3 through the water outlet opening 512, and the water inlet opening 511 and the water outlet opening 512 are respectively close to the other two opposite corners of the annular sealing ring 5.

Correspondingly, the upper rack 1 and the lower rack 2 have a rectangular structure, the first water inlet a1 and the first water outlet B1 are close to one diagonal of the upper rack 1, and the second water inlet a2 and the second water outlet B2 are close to the other diagonal of the upper rack 1.

Other contents not described in this embodiment may refer to embodiment one.

In addition to the preferred embodiments described above, other embodiments of the present invention are also possible, and those skilled in the art can make various changes and modifications according to the present invention without departing from the spirit of the present invention, which should fall within the scope of the present invention defined by the appended claims.

Claims (10)

1. The utility model provides a fluid heat exchanger, includes a plurality of heat-conducting plates that stack layer upon layer, and the front one side of heat-conducting plate is equipped with the circulation chamber that supplies liquid to flow, and the liquid in the adjacent circulation intracavity carries out the heat exchange through the heat-conducting plate, its characterized in that, the heat-conducting plate is equipped with into water intercommunicating pore and play water intercommunicating pore, and the intercommunicating pore that intakes and go out water intercommunicating pore all communicate with the circulation chamber of the front one side of heat-conducting plate, and the front of heat-conducting plate is equipped with the protruding muscle of vortex that is used.

2. The fluid heat exchanger as claimed in claim 1, wherein the heat conducting plate is provided with turbulence grooves on the back of the turbulence ribs, and the projections of the turbulence ribs and the turbulence grooves in the same flow cavity on the longitudinal section of the heat conducting plate are interlaced to form a mesh.

3. The fluid heat exchanger of claim 1, wherein the turbulating ribs are herringbone ribs, and the herringbone ribs are directed in a direction opposite to the direction of the water flow in the flow chamber; and/or the side surface of the turbulent convex rib is provided with a turbulent surface facing the water inlet communicating hole, and the included angle theta between the turbulent surface and the longitudinal section of the heat conducting plate is 100-125 degrees.

4. The fluid heat exchanger as claimed in claim 1, wherein the protrusion height h of the turbulent flow ribs is 1mm to 1.3 mm; and/or a plurality of turbulence convex ribs are arranged in parallel, the protrusion height of each turbulence convex rib is h, the center distance between adjacent turbulence convex ribs is a, wherein h/a is more than or equal to 0.25 and less than or equal to 0.45; and/or the heat-conducting plate is a metal plate, the turbulent convex ribs are formed by punching the heat-conducting plate, and the thickness S of the heat-conducting plate is 0.3-0.5 mm.

5. The fluid heat exchanger according to any one of claims 1 to 4, wherein the heat conducting plate is provided with a first flow guiding rib between the water inlet communication hole and the turbulent flow convex rib for guiding water to flow uniformly toward the turbulent flow convex rib, and the length direction of the first flow guiding rib is the same as the direction of the whole flow of the liquid in the flow cavity.

6. The fluid heat exchanger as claimed in claim 5, wherein the heat conducting plate is provided with a second flow guiding rib outside the water inlet communication hole for guiding the liquid to flow to the first flow guiding rib uniformly, and the length direction of the second flow guiding rib is the same as the radial direction of the water inlet communication hole.

7. The fluid heat exchanger according to any one of claims 1 to 4, wherein the edge of the front face of the heat conducting plate is provided with a rib located outside the turbulent flow rib, the front face of the heat conducting plate is provided with an annular groove between the rib and the turbulent flow rib, an annular seal ring is provided in the annular groove, and the adjacent heat conducting plates clamp the annular seal ring to seal the circulation chamber.

8. The fluid heat exchanger according to claim 7, wherein the outer ring side surface of the annular sealing ring is provided with a hanging buckle for limiting the inward movement of the annular sealing ring, and the hanging buckle is abutted against the outer edge of the reinforcing rib for limiting.

9. The fluid heat exchanger according to any one of claims 1 to 4, wherein the heat conducting plate is a rectangular plate, the water inlet communication hole and the water outlet communication hole are respectively arranged at two right angles of the heat conducting plate, and the water inlet communication hole and the water outlet communication hole are close to the same long side or the same diagonal of the heat conducting plate; and/or, the heat-conducting plate is rectangular board, and the both ends of heat-conducting plate are located respectively to the intercommunicating pore of intaking and the intercommunicating pore of going out, and the aspect ratio of heat-conducting plate is 1/3 ~ 1/2.

10. The fluid heat exchanger of claim 9, wherein the heat conductive plate is provided with rounded chamfers at four corners, and the rounded edges of the rounded chamfers intersect the corners of the heat conductive plate.

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