CN216205525U

CN216205525U - Cooling device

Info

Publication number: CN216205525U
Application number: CN202122550325.5U
Authority: CN
Inventors: 章辉; 章雪涛
Original assignee: Deqing Devo Thermal Technology Co ltd
Current assignee: Deqing Devo Thermal Technology Co ltd
Priority date: 2021-10-21
Filing date: 2021-10-21
Publication date: 2022-04-05
Anticipated expiration: 2031-10-21

Abstract

The utility model provides a cooling device, which comprises a working shell, a heat exchange area, a cooling medium flowing device and a heat absorption pipeline which is arranged from top to bottom along the height direction of the heat exchange area and comprises a radiating pipe consisting of a radiating straight pipe and a tubular transition piece, wherein the height of the position of a relative low side on any cross section which is relatively far forward in the direction from a relative upper part to a relative lower part of a straight channel formed by the radiating straight pipe and the transition channel formed by the tubular transition piece is lower than or equal to the height of the position of the relative low side on any cross section which is relatively far forward in the direction from the relative upper part to the relative lower part; the height of the position of the relative low side of any cross section on the straight channel communicated with the inlet of the transition channel is larger than or equal to the height of the position of the relative low side of the cross section at the inlet of the transition channel; the height of the position of the relative low side of any cross section on the straight channel communicated with the outlet of the transition channel is less than or equal to the height of the position of the relative low side of the cross section at the outlet of the transition channel.

Description

Cooling device

Technical Field

The utility model belongs to a heat exchange technical system, and particularly relates to a cooling device which is used for absorbing heat and cooling fluid with relatively high temperature flowing through the cooling device and to be heated, so that the fluid with relatively high temperature and to be heated can be converted into heated fluid with relatively low temperature when flowing out of the cooling device.

Background

Generally, because of the use requirement, a fluid to be discharged with a relatively high temperature (such as gas, liquid or a gas-liquid mixture) needs to be subjected to a temperature reduction treatment, so that the fluid after temperature reduction is applied (such as directly being changed into a finished product or being used for another purpose). Which fluid normally needs to be treated in a separate space during the cooling process.

In order to meet the cooling requirements of the fluid, a cooling device (also referred to as a heat exchange device, a cooling device, a heat absorption device, etc.) is usually adopted, and the cooling device includes a fluid conveying pipe for flowing the fluid in a relatively closed area, and the fluid conveying pipe plays a role of absorbing heat in the fluid besides playing a role of conveying the fluid, and then transmits the absorbed heat to a cooling medium (such as air, water, etc.). In order to meet the requirement of fluid cooling, the total length of the fluid delivery pipe is usually long, so that it is possible to cool the fluid flowing out of the fluid delivery pipe to a desired temperature, and since the total length of the fluid delivery pipe is long and the existing installation space (such as installation height, installation length, installation width) is limited, the fluid delivery pipe cannot be installed in a straight shape, and thus needs to be bent.

The above-mentioned bent structure can satisfy the requirement of accommodating the fluid delivery pipe with a length exceeding the installation space in a limited space, but the prior art for manufacturing the pipe cannot manufacture the integrally formed bent structure, especially for the pipe made of the material with relatively poor plasticity. A possible way to manufacture the fluid delivery tube in a bent configuration is to connect straight tubes in different directions end to end. In the use process of these components connected with the straight line pipe, part of the fluid may stay at the dead angle position in the straight line pipe when flowing through, because the fluid conveying pipe is heavy in weight usually, the staying fluid is unlikely to be discharged by a manual mode, and when a suction device is adopted, the fluid staying at the dead angle may not be sucked out, and extra energy is consumed. There is therefore a need for further improvements to existing cooling devices.

SUMMERY OF THE UTILITY MODEL

The utility model aims to solve the problems and provides a cooling device for solving the problem that a fluid possibly has a dead angle in the flowing process of a heat absorption pipeline.

In order to achieve the purpose, the utility model adopts the following technical scheme: the cooling device of the present invention comprises:

the working shell is of a closed structure;

a heat exchange region formed within the working housing;

the heat absorption pipeline is arranged from top to bottom along the height direction of the heat exchange area as a whole, at least the majority of the heat absorption pipeline is arranged in the heat exchange area, and the heat absorption pipeline is used for absorbing the heat of the fluid while the fluid flows;

the fluid inflow port is arranged on the working shell and used for allowing the external fluid to flow into the working shell and be matched with the heat absorption pipeline;

the fluid outflow port is arranged on the working shell and is used for allowing the fluid in the heat absorption pipeline to flow out to the outside;

a cooling medium flowing device which is arranged on the working shell and is used for enabling the cooling medium in a flowing state to flow along a preset cooling medium flowing direction in the heat exchange area so as to absorb heat when flowing through the heat absorption pipeline in the heat exchange area;

wherein, the heat absorption pipeline includes:

the cooling tube is followed the direction of height in heat exchange area is from the top down and is the setting of many bendings structure, and quantity is a plurality of, follows the length direction or the width direction in heat exchange area arrange and are one row or multirow, include:

a heat dissipation straight pipe;

the straight channel is formed by enclosing the inner walls of the corresponding heat dissipation straight pipes, and the height of the position of a relatively low side on any cross section which is relatively close to the front in the direction from the relatively upper part to the relatively lower part is lower than or equal to the height of the position of the relatively low side on any cross section which is positioned behind the cross section;

a tubular transition piece;

the transition channel is enclosed by the inner wall of the tubular transition piece, and the height of the position of a relative low side on any cross section which is relatively far forward from the relative upper part to the relative lower part is lower than or equal to the height of the position of the relative low side on any cross section which is behind the cross section;

in the same row of radiating pipes, a circulation gap is formed between every two adjacent radiating straight pipes which are respectively positioned on different radiating pipes, and the circulation gap is used for allowing the cooling medium to flow through; in the same radiating pipe, every two adjacent radiating straight pipes are arranged in different directions and are communicated with each other end to end in a sealing way through the tubular transition piece; the height of the position of the relative low side of any cross section on the straight channel communicated with the inlet of the transition channel is larger than or equal to the height of the position of the relative low side of the cross section at the inlet of the transition channel; the height of the position of the relative low side of any cross section on the straight channel communicated with the outlet of the transition channel is less than or equal to the height of the position of the relative low side of the cross section at the outlet of the transition channel.

Optionally, the tubular transition piece comprises:

the arc transition sections are arranged, and the arc centers of the arc transition sections are close to the corresponding heat dissipation straight pipes.

Optionally, the distance between the two ends of the tubular transition piece is not less than the outer diameter of the radiating pipe.

Optionally, the straight tube mounting through hole is formed in the working shell, and two ends of the heat dissipation straight tube extend out and then are respectively connected with one end of the corresponding tubular transition piece in a sealing mode.

Optionally, the heat dissipation straight pipe is arranged obliquely downwards along the height direction of the heat exchange area;

the range of the inclination angle formed between the heat dissipation straight pipe and the horizontal direction is 10 degrees to 30 degrees.

Optionally, any cross section on the transition channel is the same as any cross section on the straight channel in size and shape.

Optionally, any two adjacent radiating pipes in each row are staggered back and forth along the preset flow direction of the cooling medium.

Optionally, the distance between any two adjacent heat dissipation pipes in each row, which are staggered back and forth along the preset flow direction of the cooling medium, is less than or equal to the distance between two adjacent heat dissipation straight pipes on the same heat dissipation pipe and one end of the two adjacent heat dissipation straight pipes.

Optionally, the preset flow direction of the cooling medium is set from bottom to top along the height direction of the heat exchange area as a whole;

the cooling medium flow device includes:

a suction fan for extracting the cooling medium in a gaseous state;

the air outlet port is arranged on the relative upper part of the working shell;

the air inlet port is arranged at the relatively lower part of the working shell;

wherein, the suction fan is arranged on the air outlet port.

Optionally, the air outlet port is arranged at the central part of the top side of the working shell;

the air inlet port is formed in the center of the bottom side of the working shell;

wherein, the central line of air outlet port with the central line coincidence of air inlet port.

Compared with the prior art, the heat dissipation pipe with the multi-bending structure is arranged from top to bottom along the height direction of the heat exchange area, so that the fluid flowing in the heat dissipation pipe can realize the flow only by using the self weight without the help of external energy; the transition channel formed by the tubular transition piece connected with the straight radiating pipes is provided with a structure that the height of the position of the relative lower side on the cross section of any section which is relatively close to the front in the direction from the relative upper part to the relative lower part is lower than or equal to the height of the position of the relative upper part on the cross section of any section behind the section, so that no dead angle for the fluid to stay in is formed in the process of flowing through the tubular transition piece, the fluid smoothly flows through the tubular transition piece from one straight radiating pipe to the other straight radiating pipe, and the like, the fluid can finally flow out of the radiating pipe, and the fluid can not stay in the radiating pipe.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.

Fig. 1 provides a schematic structural diagram of a cooling device when a heat dissipation straight pipe and a connecting box are assembled.

Fig. 2 provides a schematic front view of the junction box of fig. 1.

Fig. 3 provides a schematic front view of a heat dissipation pipeline in a housing in an embodiment of the utility model.

FIG. 4 provides a side view of a heat sink conduit within a housing according to one embodiment of the present invention.

Fig. 5 provides a schematic side view of a heat dissipation pipeline in a housing on another side corresponding to the side in fig. 4 according to an embodiment of the present invention.

Fig. 6 provides a schematic structural view of a tubular connection element according to an embodiment of the present invention.

FIG. 7 provides a schematic representation of another tubular connection according to an embodiment of the present invention.

FIG. 8 provides a side view schematic of one side of the overall structure of one embodiment of the present invention.

FIG. 9 provides a side view schematic of another side of the overall structure of an embodiment of the present invention.

FIG. 10 provides a schematic top view of the overall structure of an embodiment of the present invention.

Fig. 11 is a schematic front view of a straight heat dissipating tube with an annular fin in a heat dissipating pipeline according to an embodiment of the present invention.

Fig. 12 provides a side view schematic of fig. 11.

Fig. 13 provides a side view of another straight heat dissipating tube with annular fins in a heat dissipating tube according to an embodiment of the present invention.

Fig. 14 provides a schematic side view of the straight radiating pipes provided with ring-shaped fins on different radiating pipes in the radiating pipeline according to an embodiment of the present invention, which are arranged at a zero-pitch.

The figures are for illustrative purposes only and are not intended to be drawn to scale. In the drawings, like reference numerals are used to indicate like elements. For purposes of clarity, not every component may be labeled in every drawing.

Detailed Description

Embodiments of the present disclosure are described herein. However, it is to be understood that the disclosed embodiments are merely examples and that other embodiments may take various and alternative forms. The figures are not necessarily to scale; some features may be exaggerated or minimized to show details of particular components. Therefore, specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a representative basis for teaching one skilled in the art to variously employ the present invention. Those skilled in the art will appreciate that various features illustrated and described with reference to any one of the figures may be combined with features illustrated in one or more other figures to produce embodiments that are not explicitly illustrated or described. The combination of features described provides a representative embodiment of a typical application. However, a particular application or implementation may require various combinations and modifications of the described features consistent with the teachings of the present disclosure.

Except where expressly indicated, all numerical quantities in this description indicating dimensions or material properties are to be understood as modified by the word "about" in describing the broadest scope of the disclosure.

Reference is made in detail to compositions, embodiments and methods of the present invention known to the inventors. However, it is to be understood that the disclosed embodiments are merely exemplary of the utility model that may be embodied in various and alternative forms. Therefore, specific details disclosed herein are not to be interpreted as limiting, but merely as a representative basis for teaching one skilled in the art to variously employ the present invention.

An example of a cooling device of the present invention includes a working enclosure, within which a heat exchange region 120 is formed, a heat dissipation pipeline for the inflow of the fluid to be discharged with relatively high temperature is installed in the heat exchange area 120 in the working housing, in addition, the working shell is also provided with a cooling medium flowing device which is used for carrying out heat exchange with the outer surface of the radiating pipeline, namely, the cooling medium flowing device absorbs the heat of the outer surface of the radiating pipeline by controlling the flow speed and the flow of the cooling medium flowing through the outer surface of the radiating pipeline in a fluid state, therefore, the fluid in the heat dissipation pipeline is cooled, and the working shell is provided with a fluid inflow port 111 for the inflow of the fluid to be dissipated with relatively high temperature and a fluid outflow port 112 for the outflow of the fluid which has dissipated heat with relatively low temperature. Accordingly, for the convenience of connection with an external pipe, a fluid inlet pipe 113 is provided at the fluid inlet port 111, and a fluid outlet pipe 114 is provided at the fluid outlet port 112.

In order to increase the heat exchange efficiency, it is conceivable to arrange the working housing in a closed structure, so that the heat exchange area 120 is also a closed area isolated from the outside by the working housing.

The heat dissipation pipe is composed of a heat dissipation pipe 210, and the heat dissipation pipe 210 is not generally set to be a straight line due to the size limitation of the heat exchange area in the working shell, but only can be set in the working shell in a plurality of bending areas 120, namely, the heat dissipation pipe 210 is bent for a plurality of times to form a structure similar to a broken line, and at this time, the heat dissipation pipe 210 includes a plurality of straight line parts of straight line segment structures.

In order to allow the fluid to flow through the heat pipe 210 by its own weight, in one example, the heat pipe 210 is bent from the top to the bottom in the height direction of the heat exchanging region 120, such that the fluid inlet port 111 is formed at a relatively upper portion of the operation housing and the fluid outlet port 112 is formed at a relatively lower portion of the operation housing. The top-down arrangement of the heat pipe 210 can achieve the fluid flow without using other devices (such as a pump), thereby simplifying the equipment and the energy required for operating the equipment. In addition, it is considered that the fluid may not flow through the heat dissipating tube 210 too fast, and if the fluid flows through the heat dissipating tube 210 too fast, the heat dissipating tube 210 may lack enough time to absorb the heat of the fluid, thereby possibly causing the temperature of the fluid flowing out of the fluid outlet port 112 to reach the set temperature.

It should be noted that, an electric pumping device (such as a pump) may be disposed on the heat dissipation pipe 210 or other pipes connected to the heat dissipation pipe 210 as required, so as to open the electric pumping device as required to control the flow rate and flow rate of the fluid in the heat dissipation pipe 210.

Since the heat pipe 210 itself absorbs heat from the fluid, the heat pipe 210 should be made of a material with good thermal conductivity (such as a solid metal material), and since economic and ecological factors are considered, stainless steel is usually selected, but other solid metal materials (such as iron and copper) may be specifically used according to the needs. In addition, it is also contemplated to dispose (e.g., electroplate) a heat conducting layer outside the heat pipe 210.

The path design of the heat dissipation pipeline can be determined according to the requirement. Generally, in order to improve the cooling effect of the heat dissipation pipe on the fluid flowing into the heat dissipation pipe during use, the length of the path is increased, and in the case of size limitation in the heat exchange area in the operating housing, the total length of the heat dissipation pipe 210 is increased by shortening the included angle between adjacent straight portions of the heat dissipation pipe 210 bent in multiple directions in the heat dissipation pipe to make a limited space, so as to increase the length of the path of the heat dissipation pipe.

Under the higher fluidic flow increase's of relative temperature the condition in getting into this heat sink, by single the heat dissipation pipeline 210 is constituteed the cooling demand can not be satisfied, and the fluidic temperature that the higher fluid of relative temperature flows out after this heat sink carries out cooling treatment promptly can not reach predetermined lower temperature relatively. Therefore, it is usually adopted to add a plurality of heat dissipation pipes 210, so that the fluid with relatively high temperature entering the cooling device can be divided, that is, the divided fluid flows into one heat dissipation pipe 210 corresponding to the divided fluid one by one, the divided fluid runs on one heat dissipation pipe 210 into which the divided fluid flows, and finally joins with other divided fluids at the fluid outlet port 112 of the cooling device.

It should be noted that, when the cooling device is configured by a plurality of the radiating pipes 210, it may be convenient for installation, and it is usually configured by arranging them in one or more rows, and the arrangement direction may be set according to needs, for example, the arrangement direction is configured by arranging them in one or more rows along the length direction or the width direction of the heat exchange area, one end ports of all the radiating pipes 210 are substantially located on one plane, and the other end ports of all the radiating pipes 210 are substantially located on another plane. In order to dispose more heat dissipation pipes 210 in the limited heat exchange area 120, the flow gap formed between two adjacent heat dissipation pipes 210 is set to a smaller size, preferably on the order of millimeters, and more preferably within 2 millimeters to 10 millimeters, under the condition that the cooling medium can pass through. Preferably, between 4 mm and 6 mm may be chosen.

It should be noted that the above-mentioned control of the size of the flow gap prevents that most of the cooling medium (especially, the cooling medium in a gaseous state) may flow to the flow gap formed by every two adjacent heat dissipation pipes 210 while avoiding the heat dissipation pipes 210 due to the excessive flow gap, which may cause the cooling medium not to be in sufficient contact with the outer surfaces of the heat dissipation pipes 210, thereby causing insufficient heat absorption of the cooling medium.

In order to solve the above-mentioned possible problems, in one example, the radiating pipes 210 in each row are arranged in a staggered manner (of course, at this time, a flow gap for flowing the cooling medium in a fluid state is still required to flow between two adjacent radiating pipes 210), and the staggered direction may be arranged according to the requirement, for example, arranged in a front-back staggered manner along the preset cooling medium flow direction a. That is, the ports of one end of every two adjacent radiating pipes 210 are not located on a plane but are arranged in a staggered manner, and the ports of one end of every two adjacent radiating pipes 210 in the extending direction of the two lateral sides of every radiating pipe 210 are located on a plane. Since the heat dissipation pipe 210 is usually disposed in a plurality of bent states, any one of the plurality of straight portions of each heat dissipation pipe 210 and the corresponding one of the plurality of straight portions of the adjacent heat dissipation pipe 210 are also disposed in a staggered manner. This arrangement allows the cooling medium to be in contact with more outer surfaces of the radiating pipe 210 while flowing, i.e., most of the cooling medium flows out through the flow gaps after flowing through the outer surfaces of the radiating pipe 210, rather than directly flowing out through the flow gaps, so that the efficiency of the cooling medium in absorbing heat is improved. In addition, compared with the original non-staggered arrangement, the resistance encountered during the flowing of the cooling medium can be reduced.

It should be noted that the preset cooling medium flowing direction a mainly refers to a direction in which a line segment connecting an inlet of the cooling medium entering the heat exchange area 120 to an outlet of the heat exchange area 120 is directed.

The distance between two adjacent radiating pipes 210 arranged in a staggered manner in the staggered direction is controlled to be less than or equal to the distance between two adjacent straight line parts on the same radiating pipe 210 and one end of the two adjacent straight line parts. Such an arrangement can achieve the purpose of interleaving while minimizing the space required for interleaving, and can achieve interleaving without changing the size of the heat exchange area 120.

The heat dissipation pipes 210 are usually made of stainless steel, and cannot be integrally formed by extrusion molding during manufacturing, but are usually composed of heat dissipation straight pipes 211 with the same size, such as multiple lengths, outer diameters, inner diameters, and the like, in a straight shape, and every two adjacent heat dissipation straight pipes 211 need to be hermetically connected through a transition connecting piece with a hollow structure.

It should be noted that the straight radiating pipe 211 is a straight portion of the radiating pipe 21 that is bent in a plurality of directions, i.e., each straight radiating pipe 211, and the transition connecting piece is an adjacent end that connects two adjacent straight portions of the radiating pipe 21.

The straight heat dissipation pipe 211 is a straight pipe in the axial direction, and the straight heat dissipation pipe 211 may have a shape such as a wave shape in the axial direction.

In addition, any two adjacent heat dissipation straight pipes 211 may be arranged in parallel. As shown in fig. 3, the included angle α may be set at an angle smaller than 90 degrees, and it is considered that the included angle α formed between two adjacent heat dissipation straight pipes 211 may be further controlled to be greater than or equal to 20 degrees and smaller than or equal to 60 degrees, specifically, 30 degrees, 40 degrees, 45 degrees, 50 degrees, or 55 degrees, in order to reduce the area formed between two adjacent heat dissipation straight pipes 211. The two adjacent heat dissipation straight pipes 211 are arranged at an included angle, so that when the heat dissipation pipe 210 is bent upward and downward, the fluid in the heat dissipation pipe 210 can flow from top to bottom spontaneously by virtue of the self gravity. After the operation is completed, the fluid will not stay in the heat dissipating pipe 210, and the fluid will finally flow out from the fluid outlet port 112, so as to avoid the situation that the fluid newly flowing into the cooling device at a later stage is not mixed with the fluid staying in the heat dissipating pipe 210 at an earlier stage, which is particularly important when the fluid is food.

As shown in fig. 1 and 2, it may be designed from the perspective of convenient installation, a conventional transition connector adopts a connection box 220 ' with a box structure, one side of the connection box 220 ' is respectively provided with an inflow connection hole 221 ' and an outflow connection hole 222 ', so that when in installation, one ends of two adjacent heat dissipation straight pipes 211 ' located in the same direction are respectively inserted into the inflow connection hole 221 ' and the outflow connection hole 222 ', and then the two heat dissipation straight pipes 211 ' are hermetically connected to the connection box 220 ' by other sealing methods such as welding. However, with the above-described connection structure of the connection box 220 ', there is a possibility that a part of the fluid may not flow out of the connection hole 222' in time after entering the connection box 220 ', but may stay in the connection box 220'. The fluid residing in the connecting box 220 'not only causes the loss of the flow of the fluid finally flowing out of the cooling device, but also causes the residual fluid residing in the connecting box 220' to have more opportunities to react with microorganisms in the air when the cooling device does not work, such as food, so that the residual fluid is fermented and the quality of the residual fluid is affected if the requirement on the quality of the fluid is higher. Furthermore, when the cooling device is operated again, the deteriorated residual fluid is mixed with the fluid newly flowing into the connection box 220', which affects the quality of the newly flowing fluid.

In addition, since the connection box 220 'is provided with the inflow connection hole 221' and the outflow connection hole 222 ', the width of the connection box 220' is necessarily required to be larger than the outer diameter of the heat dissipation straight pipes 211 ', so that when a plurality of heat dissipation straight pipes 211' are arranged, the number of the arranged heat dissipation straight pipes 211 'is limited by the size (such as width and length) of the heat exchange region 120 in the horizontal direction in the working housing, and is limited by the width of the connection box 220' besides the outer diameter. Since the width of the connection box 220 ' must be larger than the outer diameter of the straight heat dissipation pipes 211 ', the number of straight heat dissipation pipes 211 ' that can be disposed at substantially the same height in the heat exchange region 120 is reduced. This leads to the possibility of affecting the heat dissipation effect of the present heat dissipation case. The transition connector in the cooling device adopts the tubular connector 220, so that the outer diameter and the inner diameter of the tubular connector 220 can be the same as those of the heat dissipation straight pipe 211 ', and the outer diameter and/or the inner diameter of the tubular connector 220 are smaller than those of the heat dissipation straight pipe 211' according to the requirement. This allows a greater number of said heat-dissipating straight tubes 211' to be arranged in the width or length direction of the heat exchange area 120.

As an example, the transition connection piece of the heat dissipation pipe 210 connecting every two adjacent heat dissipation straight pipes 211 is a tubular connection piece 220. When the heat dissipation pipe 210 is bent from top to bottom along the height direction of the heat exchange area 120, one of the two pipe openings of the pipe connector 220 is located at the upper portion and the other pipe opening is located at the lower portion. The transition channel enclosed by the inner wall of the tubular transition piece 220 has a downward trend from top to bottom, that is, the height of the position of the relatively low side on any cross section of the transition channel, which is relatively far forward in the direction from the relatively upper part to the relatively lower part, is lower than or equal to the height of the position of the relatively low side on any cross section of the transition channel, which is behind the cross section. An upper pipe orifice of the tubular connecting member 220 is hermetically connected (e.g., by welding, flange, etc.) with an pipe orifice of an upper straight heat dissipating pipe 211 adjacent to the tubular connecting member 220, and a lower pipe orifice of the tubular connecting member 220 is hermetically connected (e.g., by welding, flange, etc.) with a pipe orifice of a lower straight heat dissipating pipe 211 adjacent to the tubular connecting member 220. In addition, in order to make the fluid flowing into the radiating pipe 210 finally flow out from the outflow end at the opposite lower end only by the self-weight of the fluid without an external power source, the following conditions should be satisfied: the height of the position of a relative low side on any cross section which is relatively close to the front in the direction from the relative upper part to the relative lower part of a straight channel which is formed by enclosing the inner wall of the heat dissipation straight tube is lower than or equal to the height of the position of the relative low side on any cross section which is positioned behind the cross section; the height of the position of the relative low side of any cross section on the straight channel communicated with the inlet of the transition channel is larger than or equal to the height of the position of the relative low side of the cross section at the inlet of the transition channel; the height of the position of the relative low side of any cross section on the straight channel communicated with the outlet of the transition channel is less than or equal to the height of the position of the relative low side of the cross section at the outlet of the transition channel.

In addition, in order to increase the total length of the single radiating pipe 210 in the limited heat exchanging area 120, the size of the area formed between the adjacent straight portions of the radiating pipe 21 bent in a plurality of ways is preferably smaller, but in order to satisfy the requirement of the cooling medium circulation, the distance between the two ends of the tubular transition member 220 is not smaller than the outer diameter of the radiating pipe 210, which is also because the tubular transition member 220 is not easy to manufacture if the distance is too small.

In addition, for convenience of installation, in one example, it may be considered that the outer diameter of the heat dissipation straight pipe 211 and the outer diameter of the tubular connection member 220 are the same. In order to make the fluid flow in the radiating pipe 210 more smoothly, the inner section of the radiating straight pipe 211 (i.e., the cross section of the straight channel) and the inner section of the tubular connector 220 (i.e., the cross section of the transition channel) may be made to have the same shape and size.

The tubular connection member 220 can have various structures, as shown in fig. 6, for example, the tubular connection member 220 includes only one arc-shaped transition section 221, and two pipe openings of the arc-shaped transition section 221 are respectively and hermetically connected with one pipe opening of the pair of straight heat dissipation pipes 211 adjacent to the arc-shaped transition section 221 when the tubular connection member is installed. As another example, as shown in fig. 7, the tubular connection member 220 includes two straight transition sections 222 and an arc transition section 221, two pipe openings of the arc transition section 221 are respectively connected with the pipe openings of the two straight transition sections 222 adjacent to the arc transition section 221 in a sealing manner, and the other two pipe openings of the two straight transition sections 222 are respectively connected with the pipe openings of the pair of straight transition sections 211 adjacent to the two straight transition sections 222 in a sealing manner during installation. As another example, the heat dissipation straight pipe comprises a straight transition section 222 and an arc transition section 221, one pipe orifice of the straight transition section 222 is connected with one pipe orifice of the arc transition section 221 in a sealing manner, the other pipe orifice of the straight transition section 222 is connected with one pipe orifice of one of the pair of heat dissipation straight pipes 211, and the other pipe orifice of the arc transition section 221 is connected with one pipe orifice of the other of the pair of heat dissipation straight pipes 211 when the heat dissipation straight pipe is installed.

To facilitate the installation of the tubular connection 220, in one example, the tubular connection 220 is disposed outside the heat exchange area 120. Specifically, a plurality of straight tube mounting through holes 115 are formed in a corresponding side of the working housing, so that two ends of each of the heat dissipation straight tubes 211 of the heat dissipation pipe 210 extend out of a pair of straight tube mounting through holes 115 corresponding to the heat dissipation straight tubes one by one, and thus two ends of one tubular connecting member 220 and two ends of each of the heat dissipation straight tubes 211 can be hermetically connected together by fixing methods such as welding. Of course, the part of the heat dissipation straight pipe 211 corresponding to the straight pipe installation through hole 115 is also fixedly connected with the working housing in a sealing manner, so as to prevent the cooling medium from flowing out of the straight pipe installation through hole 115, and influence the heat dissipation efficiency.

Because the cooling device can be also provided with a circuit device, the circuit device can normally operate. The working housing includes an inner housing 110 and an outer housing 120, and the inner housing 110 forms the heat exchange area 120, so that components of the circuit device can be on the outer housing 120, or can be disposed in a mounting area surrounded by the inner housing 110 and the outer housing 120 or a separate control box 410.

The circuit device comprises a display panel, an operation button and a control circuit board, wherein the control circuit board is also connected with various sensors for detecting the properties of the heat release fluid, the flow velocity of the flowing cooling medium, the temperature, the pressure and the like through a limited network and/or a wireless network for data transmission. For convenience of operation, display and operation components of the circuit device are disposed on an outer surface of the outer case 120, and a control circuit board is mounted in the control box 410. Of course, for convenience of installation, as shown in fig. 8, a frequency converter 420, a touch screen 430, a button 440, and the like may be provided on the control box 410.

In addition, as shown in fig. 9, a working door 121 is provided on each of a corresponding side of the outer case 120 adjacent to a corresponding side of the inner case 110 on which the tubular connection member 220 is provided. At this time, the auxiliary exhaust port 331 and the auxiliary exhaust pipe 332 may be disposed on a corresponding side of the inner case 110 on which the tubular connection member 220 is disposed. This facilitates inspection and maintenance of the tubular connector 220, the auxiliary exhaust pipe 332, and the like.

The cooling medium in the fluid state controlled by the cooling medium flowing device can be in a gas state, a liquid state or both the gas state and the liquid state.

When the cooling medium is in a gaseous state (such as air, etc. in general), the cooling medium flowing device may be used to drive the cooling medium to flow, so that the gaseous cooling medium having absorbed heat is discharged from the heat exchange region 120 through the cooling fan, and at the same time, more gaseous cooling medium with relatively low temperature outside the heat exchange region 120 is introduced into the heat exchange region 120 through the cooling fan.

When the cooling medium is in a liquid state (such as water, etc., which is commonly used), the cooling medium flowing device may be driven to flow by a cooling pump, so that the cooling medium in the liquid state, which has absorbed heat, is discharged from the heat exchange region 120 through the cooling pump, and at the same time, the cooling medium in the liquid state, which is more located outside the heat exchange region 120 and has a relatively lower temperature, is introduced into the heat exchange region 120 through the cooling pump.

It should be noted that the requirement of the cooling medium in the gaseous state for the corrosion prevention performance of the material for manufacturing the radiating pipe 210 may be lower than that of the material for manufacturing the radiating pipe 210 when the cooling medium in the liquid state is used. In addition, since the mass of the liquid cooling medium is much larger than that of the gaseous cooling medium, the work performed on the gaseous cooling medium is much smaller than that performed on the liquid cooling medium for the same distance. Whereas the same volume of liquid cooling medium absorbs more heat than does gaseous cooling medium. Based on the respective characteristics of the gaseous cooling medium and the liquid cooling medium, the selection of the cooling medium can be performed as required.

As an example, a gaseous cooling medium is used. Since the fluid inflow port 111 is provided in the relatively upper portion of the working case, the fluid outflow port 112 is provided in the relatively lower portion of the working case, the air inlet port through which the cooling medium in the gas state flows into the heat exchange region 120 is provided in the relatively lower portion of the working case, and the air outlet port through which the cooling medium in the gas state flows out of the heat exchange region 120 is provided in the relatively upper portion of the working case, in order to control the flow direction of the cooling medium to be opposite to the direction from the fluid inflow port 111 to the fluid outflow port 112, the flow direction of the cooling medium as a whole is set from bottom to top along the height direction of the heat exchange region 120. Preferably, the air outlet port is arranged at the center of the top side of the working shell; the air inlet port is formed in the center of the bottom side of the working shell; the central line of air-out opening with the central line coincidence of air inlet opening. Such a design may primarily allow for shortening the travel of the cooling medium in the gaseous state in the heat exchange area 120 to achieve the retention time in the heat exchange area 120, because the temperature of the cooling medium in the gaseous state is increased in the heat exchange area 120 due to the continuous heat absorption, and if the cooling medium in the gaseous state is left for a long time, the temperature of the cooling medium in the gaseous state may exceed the temperature of the outer surface of the radiating pipe 210, which may cause the radiating pipe 210 to absorb the cooling medium in the gaseous state in turn. Although it is also possible to increase the flow rate of the cooling medium in the heat exchange area 120 by increasing the power of the cooling fan in the cooling medium flowing device, so as to reduce the residence time of the cooling medium in the heat exchange area 120, this consumes more energy.

As shown in fig. 3 to 5 and 10, the cooling fan of the cooling medium flowing device is disposed at the top of the working housing, the cooling fan is a suction fan 310 for performing a function of sucking the cooling medium, a cooling medium inlet 351 for allowing the cooling medium in a gaseous state to enter is disposed at the bottom of the heat exchanging region 120, and a cooling medium outlet 352 for allowing the cooling medium in a gaseous state to flow out is disposed at the top of the heat exchanging region 120. In operation, as the gaseous cooling medium absorbs heat to increase its temperature, and the density of the gaseous cooling medium is lower than that of the gaseous cooling medium that does not absorb heat, the gaseous cooling medium that absorbs heat naturally flows upward, which effectively reduces the energy consumed by the suction fan 310 to absorb the upward movement of the cooling medium.

It should be noted that, the reason for the arrangement of the flow direction of the cooling medium is that the cooling medium exchanges heat with the already-released fluid with a relatively low temperature first, so as to facilitate further heat release and temperature reduction of the already-released fluid, and in the flowing process of the cooling medium, although the temperature of the cooling medium will rise due to heat absorption, the temperature of the fluid in the heat dissipation pipeline through which the cooling medium flows will also be in a trend of increasing continuously, that is, the temperature of the cooling medium is always lower than the temperature of the outer surface of the heat dissipation pipeline through which the cooling medium flows, so that it is ensured that the cooling effect of the cooling medium is ensured in the process of flowing the cooling medium in the heat exchange region 120, and the heat absorption is always performed. On the other hand, if the flow direction of the cooling medium is the same as the direction from the fluid inlet port 111 to the fluid outlet port 112, there may be a case where the temperature of the cooling medium absorbing heat in the heat exchange region 120 is higher than the temperature of the outer surface of the portion of the heat dissipation pipe in contact therewith, so that the heat on the outer surface of the portion of the heat dissipation pipe cannot be transferred to the cooling medium in contact therewith, and on the contrary, a part of the heat carried by the cooling medium in contact therewith may be absorbed, so that the heat dissipation effect is not achieved, so that the temperature of the cooling medium at the fluid outlet port 112 is higher than the temperature of the fluid flowing through the fluid outlet port 112 in the heat dissipation pipe, that is, the cooling medium may not always perform the cooling function but may perform the opposite function throughout the flowing through the heat exchange region 120, and thus a predetermined cooling effect may not be achieved.

In order to enhance the adjustment of the properties of the gaseous cooling medium in the heat exchange area 120, such as the pressure and temperature, in one example, as shown in fig. 3 to 5, an auxiliary exhaust port 331 is formed at the inner housing 110, and an auxiliary exhaust pipe 332 is correspondingly formed at the auxiliary exhaust port 331 for facilitating the exhaust and/or the connection with the external pipeline. In addition, in order to further enhance the adjustment of the gaseous cooling medium, the number of the auxiliary exhaust ports 331 is set to be several, and the auxiliary exhaust ports are uniformly distributed at intervals. The auxiliary exhaust port 331 is provided at a rear side opposite to the flow direction a of the cooling medium so that the cooling medium in a gaseous state discharged from the auxiliary exhaust port 331 can be discharged after heat exchange with the heat radiating pipe before being discharged.

In order to enhance the discharging efficiency of the gaseous cooling medium in the heat exchange area 120, as shown in fig. 3 to 5, in one example, an inverted conical suction hood 340 is provided at the inlet of the cooling fan 310.

As shown in fig. 3 to 5, in one example, when a plurality of the heat pipes 210, which are bent a plurality of times to perform a flow dividing function, are disposed in the heat exchanging region 120 in the operation housing, every two adjacent heat pipes 210 are staggered up and down in a height direction of the heat exchanging region 120. Thus, two rows of the heat dissipation tubes 210 are formed, that is, one row of the heat dissipation tubes 210 located relatively higher and one row of the heat dissipation tubes 210 located relatively lower are formed, and one of the heat dissipation tubes 210 located relatively higher or relatively lower is followed by one of the heat dissipation tubes 210 located relatively lower or relatively higher in the arrangement direction, so that the heat dissipation tubes 210 are alternately arranged in sequence. The flowing cooling medium flows through the straight portion of the radiating pipe 210 and then flows out of the fluid gap, so that the cooling medium is prevented from directly flowing out of the fluid gap without flowing through the radiating pipe 210, and the cooling effect of the cooling medium is not utilized.

Although the heat exchange area can be increased by increasing the length of the heat pipe 210 by exchanging heat between the heat pipe 210 and the flowing cooling medium, the total length of the heat pipe 210 is limited due to the space limitation of the heat exchange area 120. In order to increase the heat exchange area, it is common to add fins to the radiating pipe 210. Generally, the fins are fixedly wound in a spiral shape on the circumferential outer surface of the radiating pipe 210, which may be for the purpose of facilitating the manufacture. Such a spiral fin arrangement may prevent the cooling medium from flowing normally in the flowing direction, so that the heat on the outer surface of the portion of the radiating pipe 210 located at the back side of the spiral fin cannot be effectively carried away by the flowing cooling medium due to no or only less insufficient cooling medium passing through, and thus the radiating efficiency is affected; on the other hand, because the pitch of spiral fin can not set up owing to receiving the restriction of technology very little, pitch all sets up more than the centimetre level usually, like this under the certain circumstances of pitch, just can only be through the height that increases the fin in the unit length increase fin area, and the height of fin is because also can not set up owing to receiving the restriction of technology very big, otherwise the fin is fixed the firmness of cooling tube 210 will receive the influence, moreover owing to constantly receive the positive impact of flowing cooling medium at the during operation, it is right so to spiral fin is fixed in firmness on cooling tube 210 has just proposed higher requirement. In addition, since the height of the spiral fins is not too high due to the space limitation of the heat exchanging region 120, it is generally preferable that the height of the fins is not more than the outer diameter of the radiating pipe 210.

In order to solve the above possible problems, as shown in fig. 11 to 13, in one example, a plurality of annular fins 510 are disposed on the outer surface of the radiating pipe 210, and the annular fins 510 are disposed in parallel with each other, and the direction of the annular fins 510 is substantially the same as the direction of the flow of the cooling medium in the heat exchanging region 120, so that the direction of the heat exchanging channel 530 formed by two adjacent annular fins 510 is also substantially the same as the direction of the flow of the cooling medium in the heat exchanging region 120, thereby reducing resistance and facilitating the flow of the cooling medium in a fluid manner. In addition, the heat exchanging passage 530 formed by two adjacent ring-shaped fins 510 is formed in a ring-shaped structure around the outer surface of the radiating pipe 210, so that the cooling medium flows along the ring-shaped heat exchanging passage 530 and completely flows through the circumferential outer surface of the radiating pipe 210, thereby making it possible to contact each portion of the outer surface of the radiating pipe 210 with the flowing cooling medium.

The above-mentioned ring-shaped fin 510 is only one form of parallel fins, and as long as the condition that the fins protruded from the outer surface of the radiating pipe are parallel to each other is satisfied, other shapes of parallel fins (such as fan shape, arc shape, etc.) are also possible, and may be selected according to the need (such as heat exchange surface area, etc.). Thus, in each adjacent two of the heat exchange channels 530 formed by the parallel fins, in operation, the cooling medium can enter from the opposite rear sides of the heat exchange channels 530 in the preset cooling medium flowing direction a and can flow out from the opposite front sides of the heat exchange channels 530 in the preset cooling medium flowing direction a.

In addition, the annular fin 510 may be a single annular fin having an integral structure as shown in fig. 12, or may be a fin formed by surrounding the straight heat dissipation pipe 211 with a plurality of uniformly spaced fan-shaped fins as shown in fig. 13, and all the fan-shaped fins constituting one annular fin 510 are substantially located on the same plane.

In addition, since the parallel fins are provided on the heat dissipating pipe 210 and the heat exchanging channel 530 for the cooling medium to flow through is formed between the parallel fins, the above-mentioned function of the flow gap can be replaced by the heat exchanging channel 530, so that the distance between every two adjacent heat dissipating pipes in the same row along the preset arrangement direction is at least twice as long as the height of the parallel fins, that is, the distance between the heat dissipating pipes provided with the parallel fins can be zero when the heat dissipating pipes are arranged in a row as shown in fig. 14. It is of course also conceivable to flow out an appropriate gap, but it is necessary to control the width of the gap so as to be smaller than half of the outer diameter of the radiating pipe (i.e., the maximum value of the interval between every two adjacent radiating pipes in the same row in the preset arrangement direction is the sum of twice the height of the parallel fins and half of the outer diameter of the radiating pipe), because if it is too large, it is liable to occur that the cooling medium directly flows out through the gap without passing through the heat exchanging passage 530, resulting in an influence on the heat efficiency.

The heat exchanging channel 530 formed by the adjacent pair of the annular fins 510 is annularly surrounded on the heat dissipating tube 210, and when the heat exchanging channel 530 is operated, the cooling medium is divided into two parts along the opposite rear side of the preset cooling medium flowing direction a on the annular heat exchanging channel 530, and the two parts respectively flow along the opposite arc-shaped two sides of the heat exchanging channel 530 to the opposite front side of the heat exchanging channel 530 along the preset cooling medium flowing direction a. This allows a cooling medium, especially a cooling medium in a gaseous state, to flow through both lateral sides of the radiating pipe 210 at the same time when flowing, i.e., it is substantially possible to achieve that most of the outer surface of the radiating pipe can have the cooling medium flow therethrough to exchange heat therewith.

In order to reduce the resistance to the flowing cooling medium, the cooling channel is arranged in a direction parallel to the preset flow direction of the cooling medium. The cooling medium, which is advantageously flowed, is discharged in time after absorbing heat from the heat dissipating pipe 210, and is left in the heat exchanging region 120 for a long time, and is then heated to a temperature higher than that of the outer surface of the heat dissipating pipe 210 when absorbing excessive heat, so that the direction of heat transfer is reversed.

It should be noted that the height of the parallel fins is not limited to the size of the total heat exchange area required. In addition, the height is also inversely proportional to the distribution density of the parallel fins on the radiating pipe 210, that is, the height of the parallel fins is inversely proportional to the distance between every two adjacent parallel fins.

Specifically, taking the ring fins 510 as an example, the distance between two adjacent ring fins 510 may be controlled to be in the millimeter range, optionally 8 mm, 5mm, 3 mm, 2 mm, and even 1mm, and the ring fins 510 may be fixed on the outer surface of the radiating pipe 210 by welding (e.g., laser welding) or other fixing methods. Compared to the above spiral fin, the total area of the ring fin 510 within one pitch may be doubled to the total area of the spiral fin with the same fin height, so that it is possible to multiply the heat exchange area.

The area S1 of the spiral fin and the area S2 of the ring fin 510 wound around the radiating pipe 210 when the height of the fin is the same and the length is 1 pitch are calculated as follows:

since the radiating pipe 210 is generally cylindrical, the area S1 of the fin spirally wound around the radiating pipe 210 is calculated by:

s1 is n × L × H, n is the number of turns of the helix, L is the length of the single turn of the helix, and H is the height of the fin;

L＝sqrt((πD)^2₊p ^2), D is the outer diameter of the heat dissipation tube 210, and P is the thread pitch;

from the above, the area of the helical fin with 1 pitch is:

S1＝1×sqrt((πD)^2₊P^2)×H＝sqrt((πD)^2₊P^2)×H；

S2＝πR^2×([P÷(δ₊s)]+1) x H, R is the outer radius of the heat dissipation tube 210 being wound, P is the pitch, δ is the thickness of the fins, and s is the distance between two adjacent fins;

assuming that P is 20mm, δ is 1mm, S is 5mm, and P ═ D, then 3 to 4 ring fins 510 (here 4) can be placed in a P, i.e., S2 has a value of 4H π R ^2 ^ H π D ^2 and S1 ^ HD (sqrt (π ^2)₊1) H pi D, it can be seen that the heat exchange area is greatly increased after the annular fin 510 is arranged. This can realize that the ratio of S1 to S2 is greater than 1 and equal to or less than 4. Thereby realizing that no extra addition is addedThe heat exchange area is increased in multiples in the case of the installation space.

Further, knowing D and P, the cylindrical outer surface area with an outer diameter D and a height P can be calculated:

S3＝π×D×P；

comparing S1 and S3, the size of both is substantially within one grade, when P is less than H, S3 is less than S1, i.e. the area of one radiating surface of the helical fin is greater than the external surface area of the cylindrical radiating pipe 210 carrying the helical fin, moreover, there are two radiating surfaces with the same area on the helical fin.

And because the height that the fin can not set up is too big, not only extravagant, has proposed higher requirement moreover to the fin with the firm degree of connection of cooling tube, for above-mentioned reason, the height range of fin is for being no less than the quarter of the external diameter of cooling tube and be not more than the external diameter of cooling tube.

In operation, the temperature reduction is usually achieved by using only gaseous cooling medium, i.e. gaseous cooling medium flows in the heat exchange area 120 in the opposite direction to the flow of the heat-releasing fluid. In the above, the heat-releasing fluid flows in from the fluid inflow port 111 at the relatively upper portion and flows out from the fluid outflow port 112 at the relatively lower portion, and the gaseous cooling medium flows out from the relatively upper portion after entering the heat exchange region 120 from the relatively lower portion. But may sometimes be influenced by environmental factors (e.g., temperature of air as a gaseous cooling medium), operational requirements (e.g., temperature of fluid flowing into the fluid inlet port 111, predetermined fluid outlet temperature), etc., and it may happen that the temperature of fluid flowing out of the fluid outlet port 112 is still higher than the predetermined fluid outlet temperature.

In order to solve the above-mentioned possible problem that the temperature of the fluid flowing out of the fluid outflow port 112 is still higher than the predetermined temperature, as shown in fig. 4, 5 and 8, in one example, a spray device is provided in the heat exchange region 120 near the fluid outflow port 112, the spray device can be used for absorbing a liquid cooling medium (such as water) having a better heat efficiency than a gaseous cooling medium such as air, the spray device includes a spray pipe 361 and a plurality of atomizing nozzles 362 provided on the spray pipe 361, the motive force for flowing the cooling medium in a liquid state is provided by a high-pressure atomizing pump 363, and the opening and closing and the power adjustment of the high-pressure atomizing pump 363 can be controlled by the circuit device, the atomizing nozzles 362 are provided below the heat dissipation pipe 210, and the spray ports on the atomizing nozzles 362 are aligned with the heat dissipation pipe 210. Thus, the portion of the heat dissipating pipe 210 near the fluid outlet port 112 is sprayed with the liquid cooling medium having higher heat absorption efficiency to rapidly cool the fluid sprayed into the heat dissipating pipe 210 and finally reach the predetermined fluid outlet temperature.

It should be noted that the high-pressure atomizing pump 363 is only one of the cooling pumps, and other types of pumps can be provided as required by those skilled in the art. The atomizer 362 is disposed below the heat pipe 210 to cool the heat-releasing fluid to be discharged, so as to effectively control the discharge temperature of the fluid. In addition the setting position of the atomizer 362 makes the sprayed liquid cooling medium only need to cool the heat dissipation straight pipe 211 located at the lowest layer in the heat dissipation pipe 210, rather than spraying the whole heat dissipation pipe 210, which not only saves the electric power consumption required by spraying, but also is beneficial to saving the consumption of the liquid cooling medium. In addition, the atomizing spray also plays a positive role in reducing the consumption of the cooling medium in a liquid state.

In addition, in order to facilitate the collection of the liquid cooling medium sprayed from the atomizing nozzle 362 after absorbing heat with the heat dissipating pipe, as shown in fig. 5, a liquid cooling medium collecting tank 364 is disposed below the spray pipe 361 in one example. This not only serves to facilitate the collection but also provides a basis for recycling the cooling medium in liquid form.

In addition, as shown in fig. 4, in one example, the length of the shower pipe 361 is substantially the same as one dimension (such as length, width or height) of the heat exchange area 120, and it is also conceivable to arrange the length direction of the shower pipe 361 to be consistent with the arrangement direction of the heat dissipation pipes 210, so that the number of the atomizing nozzles 362 arranged on each shower pipe 361 can be the same as the number of the heat dissipation pipes 210 and one-to-one correspondence can be arranged just below one of the heat dissipation pipes 210 corresponding to the same.

In the claims, the word "comprising" does not exclude other elements or steps; the word "a" or "an" does not exclude a plurality. Use of ordinal terms such as "first," "second," etc., in the claims to modify a claim element does not by itself connote any priority, order, or temporal order of execution of one claim element over another, but are used merely for distinguishing one claim element from another. Although certain features may be described in different dependent claims, this does not imply that these features cannot be used in combination. Various aspects of the present invention may be used alone, in combination, or in a variety of arrangements not specifically discussed in the embodiments described in the foregoing and is therefore not limited in its application to the details and arrangement of components set forth in the foregoing description or illustrated in the drawings. For example, aspects described in one embodiment may be combined in any manner with aspects described in other embodiments. The steps, functions or features recited in a plurality of modules or units may be performed or satisfied by one module or one unit. The steps of the methods disclosed herein are not limited to being performed in any particular order, as some or all of the steps may be performed in other orders. Any reference signs in the claims shall not be construed as limiting the scope of the claims.

While the utility model has been described by way of illustration and example, such description and illustration should be considered illustrative or exemplary and not restrictive. Those skilled in the art will appreciate that various modifications, additions and substitutions are possible, without departing from the scope and spirit of the utility model as disclosed in the accompanying claims.

Claims

1. A cooling device, characterized by, the cooling device includes:

the working shell is of a closed structure;

a heat exchange region formed within the working housing;

wherein, the heat absorption pipeline includes:

a heat dissipation straight pipe;

a tubular transition piece;

2. The cooling device of claim 1, wherein the tubular transition piece comprises:

3. The cooling device of claim 2, wherein:

the distance between the two ends of the tubular transition piece is not less than the outer diameter of the radiating pipe.

4. The cooling device of claim 2, further comprising:

and the straight pipe mounting through hole is formed in the working shell, and the two ends of the heat dissipation straight pipe extend out and then are respectively connected with one end of the corresponding tubular transition piece in a sealing manner.

5. The cooling device of claim 1, wherein:

the heat dissipation straight pipe is arranged obliquely downwards along the height direction of the heat exchange area;

6. The cooling device according to any one of claims 1 to 5, wherein:

any cross section on the transition channel is the same as any cross section on the straight channel in size and shape.

7. The cooling device according to any one of claims 1 to 5, wherein:

any two adjacent radiating pipes in each row are arranged in a front-back staggered manner along the preset flow direction of the cooling medium.

8. The cooling device of claim 7, wherein:

and the distance between any two adjacent radiating pipes in each row along the preset cooling medium flowing direction and arranged in a staggered manner from front to back is smaller than or equal to the distance between two adjacent radiating straight pipes on the same radiating pipe and one end of the adjacent radiating straight pipes.

9. The cooling device according to any one of claims 1 to 5, wherein:

the whole preset flow direction of the cooling medium is arranged from bottom to top along the height direction of the heat exchange area;

the cooling medium flow device includes:

a suction fan for extracting the cooling medium in a gaseous state;

wherein, the suction fan is arranged on the air outlet port.

10. The cooling device of claim 9, wherein:

the air outlet port is arranged at the center of the top side of the working shell;