JP6454915B2 - Cooling heat transfer device - Google Patents

Description

  The present invention is directed to a cooling heat transfer device in which a refrigerant circulation frame is provided radially in order to cool the heat transferred from the heating element.

  When the cool heat transfer device comes into contact with the heating element, the transmitted heat is about to be conducted in the same direction along the contact surface.

  However, in the prior art, as shown in Patent Documents 1 and 2, heat pipes that contact the heating elements are arranged in a predetermined longitudinal direction, and in such an arrangement state, heat to be cooled is obtained. It does not mean that the transmission area is effectively set along the plane direction.

  On the other hand, in the case of Patent Documents 3 and 4, the heat pipes are arranged radially, and compared with the case of Patent Documents 1 and 2, the heat transfer region to be cooled is aligned along the plane direction. It is superior to the configurations of Patent Documents 1 and 2 in terms of effective use.

However, in the configurations of Patent Documents 3 and 4, as shown in FIG. 10 , the heat-cooling fins 2 project from the upper side of the above-described radial plane, and the cooling air from the fan is Even though it enters the area sandwiched between the two, it is impossible to move in the plane direction. By filling the area where the heat pipe is installed, backflow is generated on the blower side, and efficient cooling is performed. I can't.

  However, it is conceivable to prevent the above-mentioned backwind by blowing the cooling air from the side of the side where the cooling fins are projected, but when setting a radial heat pipe, the side space In many cases, it is impossible to blow sufficient cooling air.

  If conforming to such a prior art, on the one hand, the heat transmitted from the heating element 4 is transmitted not in the longitudinal direction but radially, while the cooling air from the fan is blown to the heat pipe side, The basic configuration that realizes efficient thermal cooling due to the extremely low degree of occurrence has not been proposed to date.

WO2011 / 122332 publication JP 2014-159915 A JP 2001-251073 A JP 2003-283172 A

  The present invention achieves a high cooling effect by transferring the heat transferred from the heating element in a radial manner while reducing the degree of back wind generated even when cooling air is blown to the heat pipe. It is an object of the present invention to provide a configuration of a heat transfer device for cooling that can be performed.

  In order to solve the above-described problems, the basic configuration of the present invention is a radial configuration from a central refrigerant circulation frame disposed at a central position in the planar direction along a direction in which an adhesive surface for a heating element can be formed or a position in the vicinity thereof. Three or more radial refrigerant circulation frames are disposed on the outer periphery, and an outer refrigerant circulation frame is disposed around the outer periphery of each radial refrigerant circulation frame, and the central refrigerant circulation frame and the radial refrigerant circulation frame communicate with each other in the adjacent region. And the radial refrigerant circulation frame and the outer refrigerant circulation frame form a heat pipe by connecting the adjacent areas to each other, and each outer refrigerant circulation frame, each radial refrigerant circulation frame, and the central refrigerant circulation frame, A state in which the heat-releasing fins are made to have the same width as each of the radial refrigerant circulation frames along the direction orthogonal to the planar direction in the region surrounded by, and a gap is formed along the planar direction. Install in In both the enclosed states, the heat cooling fins in the region are installed in a state where each radial refrigerant circulation frame and the central refrigerant circulation frame are connected to each outer refrigerant circulation frame. It consists of a transmitter.

  In the present invention having the above-mentioned basic configuration, the heat transmitted from the heating element is transmitted to the radial refrigerant circulation frame, so that the heat conduction region to be cooled is wider than in the case of Patent Documents 1 and 2. On the other hand, efficient cooling is achieved, but even if the cooling air is blown from the upper side of the heat pipe by the fan, the cooling air remains between the heat cooling fins forming a gap in the plane direction. By passing, it is possible to achieve efficient thermal cooling while setting the state where the back wind is generated to be extremely low as compared with the case of Patent Documents 3 and 4.

The basic structure is shown, (a), (b), (c) is a top view, (d) is a sectional side view along AA of (a). Embodiment which formed the uneven surface in the wall part of each refrigerant | coolant circulation frame is shown, (a) is a top view at the time of forming the uneven surface curved along the plane direction, (b) is a plane direction It is a top view at the time of forming a polygonal uneven surface along, and (c) and (d) form an uneven surface which has a portion which intersects perpendicularly with a longitudinal direction along a direction perpendicular to the plane direction and the plane direction. It is drawing of the direction orthogonal to the plane view and elevation in the case where it did, ie, the said plane direction. An embodiment in which the wall portions of the radial refrigerant circulation frame and the outer refrigerant circulation frame of the basic configuration are in a meandering state, a parallel broken line shape, or a zigzag state including a region perpendicular to the longitudinal direction is shown. It is a meandering plan view, (b) is a polygonal plan view, and (c) is a zigzag plan view. The embodiment which the unevenness surface formed the fin for heat cooling has shown, (a) shows the case of the uneven surface along a plane direction, (b) shows the case of the uneven surface of the direction orthogonal to the said plane direction Indicates. The heat-dissipating fin is divided by a plurality of plate-like pieces in a direction perpendicular to the plane direction, and adjacent plate-like pieces in the direction perpendicular to the plane direction are set at different positions along the plane direction. 1A is a sectional view in a direction orthogonal to the planar direction, and FIG. 2B is a partial perspective view. Embodiment which provided the grating | lattice by crossing the fine beam to the partial area | region of each refrigerant | coolant circulation frame is shown, (a) is a top view, (b) is a sectional side view. The sectional side view at the time of laminating | stacking the heating element and the heat exchanger for cooling of a basic composition is shown. The side sectional view of the embodiment in which the fan is provided on the side where the heating element does not exist is shown, and the dotted line on the right side shows the fixing mesh laid between the fan housing fixing frame and the central axis, A solid line indicates a beam constructed between the fan housing fixing frame and the central axis. The perspective view which shows the process of the Example which manufactures the heat exchanger for cooling of a basic structure is shown. The side view which shows the structure of a prior art is shown.

Basic configuration, FIG. 1 (a), (b) , (c), (d), the relative central refrigerant frame 11 which receives the transfer of heat from the heating element 4, three or more radially refrigerant The frame 12 is disposed after the adjacent areas are in communication with each other, and as shown in FIGS. 1 (a), (b), (c), and (d), each outer refrigerant circulation frame 13 and each radial refrigerant. In the region surrounded by the circulation frame 12 and the central refrigerant circulation frame 11, the heat cooling fins 2 have the same width as each radial refrigerant circulation frame along the direction orthogonal to the planar direction. In the state where the fins for heat cooling in the region are connected to each radial refrigerant circulation frame 12 and the central refrigerant circulation frame 11 and each outer refrigerant circulation frame 13 in the enclosed state. It is erected.

  In order to allow the cooling air to pass through, the heat-dissipating fins 2 form a gap therebetween in the plane direction.

In the basic configuration, normally, as shown in FIGS. 1 (a), (b), (c), and (d), the heat-dissipating fins 2 are protruded further outside the outer refrigerant circulation frame 13. The structure which further promotes cooling efficiency is employ | adopted by adoption of embodiment characterized by the above-mentioned.

  “Radial” in the basic configuration refers to a state in which the radial refrigerant circulation frame 12 extends in two or more directions with respect to the central refrigerant circulation frame 11, but “the center position or a position in the vicinity thereof” This is to achieve a state in which the heat transfer state in the radial refrigerant circulation frame 12 extending in two or more directions is almost uniform.

The heat cool radiation fins 2 which connects to the outer refrigerant circulation frame 13, FIG. 1 (a), (b) such as linear, and either crossed linear as well FIG. 1 (c) It can be adopted.

Outer refrigerant frame 13 is FIG. 1 (a), in the case of forming the sides (b), a polygonal shape as in (c) (rectangular), radial coolant circulation frame 12, FIG. 1 (a), ( as in b), configured to extend up to the corner of the polygonal shape, and as shown in FIG. 1 (c), selected as an embodiment of the "radial" for any configuration to extend to an intermediate portion of each side be able to.

  Each refrigerant circulation frame in the basic configuration is in a vacuum state, the refrigerant is in a liquid state on the lower side, the liquid refrigerant evaporates by heat transmitted from the heating element 4, and the upper side is filled with an evaporator. The mutual circulation state is realized by the rise accompanying the evaporation of the lower liquid and the fall accompanying the liquefaction of the upper liquid.

  In the basic configuration, by arranging a plurality of refrigerant circulation frames in a radial manner, as compared with the case where heat is transmitted to the heat pipes 1 on both sides in the longitudinal direction of the heating element 4 as in Patent Documents 1 and 2. In addition, by diffusing heat through the communication state of the regions adjacent to at least three radial refrigerant circulation frames 12, the region to be cooled through the heat-dissipating fins 2 can be expanded. Efficient heat cooling can be realized.

  In order to explain the above matter in accordance with the general formula of thermodynamics, in the radial refrigerant circulation frame 12, since the stored liquid refrigerant hardly moves in the plane direction, the differential equation of heat conduction in the refrigerant is: When there is no internal heat generation source, it can be expressed by the following partial differential equation according to the temperature θ, the time t, and the distance x in the length direction (for example, Nobuhiro Seki) "Heat transfer engineering": 4 pages, published on December 20, 2002 by Morikita Publishing Co., Ltd.).

（θ_ｆ：周囲の環境温度、ｆ：前記平面方向と直交する方向における液状冷媒の断面積、ｐ：液状冷媒の断面に沿った周囲の長さ、α：液状冷媒の熱伝達率、λ：液状冷媒の熱伝導率、ｈ＝λ／ｃρ：液状冷媒の温度伝導率、
ｃ：液状冷媒の比熱、ρ：液状冷媒の密度、λ：液状冷媒の熱伝達率）

(Θ _f : ambient temperature, f: cross-sectional area of the liquid refrigerant in a direction perpendicular to the plane direction, p: length of the circumference along the cross-section of the liquid refrigerant, α: heat transfer coefficient of the liquid refrigerant, λ: Thermal conductivity of liquid refrigerant, h = λ / cρ: temperature conductivity of liquid refrigerant,
c: specific heat of liquid refrigerant, ρ: density of liquid refrigerant, λ: heat transfer coefficient of liquid refrigerant)

Here, based on the environmental temperature θ _f as a reference, the steady heat conduction when θ−θ _f of the partial differential equation is set to θ is ∂θ / ∂t = 0.

（但し、ｍ^２＝ｐα／λｆ）

(However, m ² = pα / λf)

  From the general solution of the above equation (1), in the radial refrigerant circulation frame 12, when the distance from the end of the central refrigerant circulation frame 11 is x,

を得ることができる（但し、ｋ_１、ｋ_２は、境界条件によって特定される係数）。

(Where k ₁ and k ₂ are coefficients specified by the boundary conditions).

As long as the temperature of the refrigerant cannot increase as it moves away from the heating element 4, k ₁ = 0, and when the average temperature of the liquid refrigerant in the central refrigerant circulation frame 11 is θ _b ,

という一般解を得ることができる。

The general solution can be obtained.

  Therefore, in one radial refrigerant circulation frame 12, the amount of heat q transferred from the central refrigerant circulation frame 11 via the liquid refrigerant is

が成立する。

Is established.

  Therefore, when the number of the radial refrigerant circulation frames 12 is N, the total amount of heat Q transferred from the central refrigerant circulation frame 11 to the refrigerant in each radial refrigerant circulation frame 12 is:

が成立することに帰する。

Is attributed to

  In the case of Patent Documents 1 and 2, N = 2 because heat is sequentially transferred in the longitudinal direction on both sides of the heating element 4, whereas in the case of the basic configuration, N ≧ 3. It becomes possible to expand the heat transfer area to be cooled via the heat-dissipating fins 2 and to set a large amount of heat energy to be cooled.

  Hereinafter, description will be given in accordance with each embodiment.

In the present invention, the inner side surfaces of all or any of the radial refrigerant circulation frame 12 according to claim 1 and the radial refrigerant circulation frame 12 according to claim 2 and the outer refrigerant circulation frame 13 are longitudinal in the plane direction. As shown in FIG. 2 (a), a curved uneven surface is formed, or as shown in FIG. 2 (b), a fold line-shaped curved surface is formed, or shown in FIG. 2 (c). Thus, an embodiment characterized by forming an uneven surface having a region portion orthogonal to the longitudinal direction can be adopted.

In particular, FIG. 2 (c), the (d), the all or part of the inner surface of the wall of the central refrigerant frame 11 and radially refrigerant frame 12 and the outer coolant circulation frame 13 is the plane direction Of course, the embodiment in which the uneven surface is formed also in the orthogonal direction can be adopted.

In the above embodiment shown in FIGS. 2 (a), (b), (c) and (d), the area of the wall is increased, and as a result, the amount of heat transferred to the installed heat-dissipating fin 2 And the cooling efficiency can be improved.

Further in the above embodiments, either all or a portion of the inner surface of the wall portion forms an uneven surface by meandering curved state as shown in FIG. 3 along the longitudinal direction in the planar direction (a), or As shown in FIG. 3 (b), an uneven surface with parallel broken lines is formed, or as shown in FIG. 3 (c), an uneven surface with a zigzag state having a region portion orthogonal to the longitudinal direction is formed. When the embodiment characterized by the above is adopted, the distance between the radial refrigerant circulation frame 12 and / or the outer refrigerant circulation frame 13 is increased. As a result, the installed cooling fin is The amount of heat to be transmitted can be increased and efficient cooling efficiency can be achieved.

In the basic configuration, as the thermal cooling fins 2 shown in FIG. 4 (a), or to form an uneven surface along a planar direction, or as shown in FIG. 4 (b), perpendicular to the planar direction An embodiment characterized in that a concavo-convex surface is formed along the direction to be performed can be adopted.

Figure 4 (a) shows the case of curved uneven surfaces, FIG. 4 (b) shows a case of a zigzag uneven surface by folding, in these embodiments, to increase the area of the fin Thus, the cooling efficiency can be improved.

  In particular, when an uneven surface is formed in a direction orthogonal to the plane direction, the cooling air blown from the upper fan and the heat cooling fin 2 collide with each other, and the plate-shaped heat cooling fin Compared to the case 2, the contact time with the cooling air becomes longer, so that remarkable cooling efficiency can be achieved.

In the basic configuration, FIG. 5 (a), the (b), the forms a plurality of plate-shaped pieces along a direction thermal cooling fins 2 are perpendicular to the planar direction, adjacent Embodiments characterized in that the plate-like pieces are arranged at different positions along the plane direction can be adopted.

5 (a) shows an embodiment in which the direction orthogonal to the planar direction than the planar direction and the thickness, FIG. 5 (b), thicker than the direction in which the direction of the plane direction perpendicular to the planar direction In the above embodiments, the cooling air that has passed through the gap in a predetermined stage in the vertical direction is shown as having a thickness and the end portions exhibit a pair of coupled states along the planar direction. In the next stage, a turbulent flow is formed by colliding with the heat-dissipating fins 2 and the contact time with the cooling air is prolonged as compared with the flat heat-dissipating fins 2. Can be improved.

In the basic configuration, as shown in FIG. 6 (a), (b) , in some or all regions of the refrigerant circulating frame, in a direction perpendicular to the planar direction and the planar direction was laid a fine beam Accordingly, an embodiment characterized in that a capillary channel region in the form of a lattice 3 can be adopted.

  By forming such a grid-like capillary channel region, the evaporated refrigerant collides with the beam forming the grid, and as a result, the heat-cooling fins installed between the refrigerant circulation frames. The amount of heat transferred to 2 can be increased, and the cooling effect can be further improved.

In the basic configuration, as shown in FIG. 7 , it is possible to employ a configuration in which heat-removing heat transfer devices are sequentially stacked.

FIG. 7 shows a stacked state in which the heating elements 4 are in contact with all the cooling heat transfer devices, but the heating elements 4 correspond to some cooling heat transfer devices. Naturally, it is possible to adopt an embodiment in which the heating element 4 is in contact, and further, a stacked state in which the heating element 4 is in contact with the lowermost heat transfer device for cooling.

  In addition, in the said lamination | stacking, in order to back flow of cooling air as much as possible, it is good to laminate | stack so that each radial refrigerant | coolant circulation frame 12 and the outer side refrigerant | coolant circulation frame 13 may become the same position along a plane direction.

  With such a laminated state, in the above-described embodiment, the cooling area can be expanded, and further improvement in cooling efficiency can be achieved.

  As is apparent from the general formula of [Equation 4], the temperature of the liquid refrigerant decreases as it moves away from the central refrigerant circulation frame 11, and as a result, the amount of liquid refrigerant stored below increases. Tend to do.

  Therefore, in the basic configuration, when the embodiment characterized in that the refrigerant inlet is provided in the opposite side position in contact with the heating element 4 in the central refrigerant circulation frame 11, the liquid refrigerant is stored at a high level. Therefore, the tendency to increase as the distance from the central refrigerant circulation frame 11 is alleviated, and hence the unevenness of the evaporation state of each refrigerant circulation frame can be reduced.

  The cooling heat transfer device according to the present invention includes a case in which a fan for circulating cooling air between the heat cooling fins 2 is installed on the side where the heating element 4 is bonded, or on the opposite side. Both of the cases where they are not installed at these positions can be employed.

However, when installing, as shown in FIG. 8 , the fan 6 is often installed on the side where the heating element 4 is not bonded.

Actually, in order to couple the fan 6 to the cooling heat transfer device, as shown in FIG. 8 , a fan housing fixing frame 81 is provided around the outside of the fan 6, and the fan housing fixing frame 81 and the fan 6 are provided. A fixing mesh 71 or a plurality of beams 72 are installed between the rotating shaft 91 and a central shaft 92 that rotatably supports the rotating shaft 91, while the cooling heat transfer device is supported around the outside of the cooling heat transfer device. In many cases, an embodiment in which the fixed frame 82 is provided and both the fixed frames are joined via the spacer 10 is adopted.

  Since each refrigerant circulation frame forms a hollow state on the inner side, it is impossible to mold at once.

  However, according to the following embodiments, it is possible to realize the cooling heat transfer device having the basic configuration.

As shown in FIG. 9 , the embodiment is characterized in that a heat-cooling transmitter having the basic configuration (2) based on the manufacturing process according to the following order is manufactured.
(1) A surface plate for the central refrigerant circulation frame 11 located on the side opposite to the side in contact with the heating element 4, a surface plate for the radial refrigerant circulation frame 12, a surface plate for the outer refrigerant circulation frame 13, and the installed heat Forming one surface plate for bonding constituted by plate-like pieces for cooling fins 2 by a die, a punching press, or etching;
(2) Inner intermediate plate-like piece for the central refrigerant circulation frame 11, intermediate plate-like piece for the radial refrigerant circulation frame 12, intermediate plate-like piece for the outer refrigerant circulation frame 13, and a plate shape for the cooling fin to be installed. A step of forming a plurality of bonded intermediate plates formed by a piece by a die, a punching press, or etching,
(3) A back plate for the central refrigerant circulation frame 11 positioned on the side in contact with the heating element 4, a back plate for the radial refrigerant circulation frame 12, a back plate for the outer refrigerant circulation frame 13, and a built-in heat release. A step of forming one bonded back plate constituted by plate-like pieces of cooling fins 2 by a die, a punching press, or etching;
(4) (1) one coupling surface plate, (2) plural coupling intermediate plates, and (3) one coupling back plate are sequentially laminated and tightened or joined by screws. The process of adhering to each other by welding accompanying the diffusion of the melted components.

  By adopting the steps based on the order of (1) to (4) above, it is possible to efficiently manufacture a cooling heat exchanger having a basic configuration with each refrigerant circulation frame having a hollow state.

The manufacturing method of embodiment can also be naturally adapted in each embodiment as shown in FIG. 2, 3, 4, 5.

  INDUSTRIAL APPLICABILITY The present invention can realize efficient air cooling in an apparatus having many heating elements such as an automobile and a computer, and its utility value is tremendous.

DESCRIPTION OF SYMBOLS 1 Heat pipe 11 Central refrigerant | coolant circulation frame 12 Radial refrigerant circulation frame 13 Outer refrigerant circulation frame 2 Heat cooling fin 20 Outer heat cooling fin 3 Grid 4 Heating element 5 Heat sink 6 Fan 71 Fixing mesh 72 Beam 81 Fixing and fixing fan Frame 82 Cooling frame support fixing frame 91 Rotating shaft 92 Center shaft 10 Spacer

Claims (4)

    Three or more radial refrigerant circulation frames are arranged radially from a central refrigerant circulation frame arranged at or near a central position in the plane direction along the direction in which an adhesive surface to the heating element can be formed, In addition, an outer refrigerant circulation frame is disposed around the outer periphery of each radial refrigerant circulation frame, the central refrigerant circulation frame and the radial refrigerant circulation frame are in communication with each other in adjacent regions, and the radial refrigerant circulation frame and the outer refrigerant circulation frame are mutually connected. A heat pipe is formed in a region surrounded by each outer refrigerant circulation frame, each radial refrigerant circulation frame, and the central refrigerant circulation frame. The width is set equal to each radial refrigerant circulation frame along a direction orthogonal to the planar direction, and is constructed in a state in which a gap is formed between the radial refrigerant along the planar direction. Heat inside Cold fins is a heat transfer device for cooling that is spanned in a state of connecting the respective radial coolant circulation frame and central refrigerant circulation frame and the outer refrigerant frame.   The heat-cooling heat transfer device according to claim 1, wherein the heat-cooling fins protrude from the outer refrigerant circulation frame.   The fan for generating the cooling air which distribute | circulates between the fins for thermal cooling is installed in the position where the heating element is adhere | attached, or the position on the opposite side. The heat exchanger for cooling as described in any one of 2. The manufacturing method of the heat exchanger for natural cooling of Claim 1 by the manufacturing process according to the following orders.
(1) A surface plate for a central refrigerant circulation frame, a surface plate for a radial refrigerant circulation frame, a surface plate for an outer refrigerant circulation frame, and a heat-dissipating fin that is installed on the side opposite to the side in contact with the heating element Forming one surface plate for bonding constituted by plate-like pieces for molding by a die, a punching press, or etching;
(2) Molded by an inner intermediate plate piece for the central refrigerant circulation frame, an intermediate plate piece for the radial refrigerant circulation frame, an intermediate plate piece for the outer refrigerant circulation frame, and a plate member for the cooling fins to be installed. Forming a plurality of bonded intermediate plates by a mold, a punching press, or etching,
(3) The back plate for the central refrigerant circulation frame, the back plate for the radial refrigerant circulation frame, the back plate for the outer refrigerant circulation frame, and the heat-dissipating fins installed on the side in contact with the heating element A step of forming one bonded back plate constituted by plate-like pieces by a mold, a punching press, or etching;
(4) (1) one coupling surface plate, (2) plural coupling intermediate plates, and (3) one coupling back plate are sequentially laminated and tightened or joined by screws. The process of adhering to each other by welding accompanying the diffusion of the melted components.

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