JPS6257240A - Heat pipe type heat radiator - Google Patents

Abstract

PURPOSE:To provide a high performance heat radiator, which indicates a very low thermal resistance value and very quick thermal response, by implementing the high performance of heat receiving and radiation by providing many small-diameter heat pipes. CONSTITUTION:Inserting and connecting holes 4 for inserting and connecting the heat absorbing parts of heat pipes 2 are provided between the inside of a block in parallel with a heat receiving plane and also in parallel one another from a plurality of the side surfaces of the block. The inserting and connecting hole group, which is formed from one side surface viewed from the side of the heat receiving plane is made to cross the inserting and connecting hole group, which is provided from the other side surface without fail. When viewed from the side surface, the groups never cross to each other. The inserting and connecting hole groups are formed from the upper side surface and the right side surface of a heat receiving metal block 1. In both side surface, 64 holes are provided in four columns and in eight stages all together. The heat absorbing parts of the heat pipes are closely inserted and connected in the inserting and connecting hole group 4 in the heat receiving metal block. The heat transfer parts of the heat pipes are suitably bent or made to remain straight. Thus, the heat radiating parts of the heat pipes are guided into the specified positions of the heat exchange parts of the heat radiator and arranged into pipe group alignment in specified stage columns. In this way the heat exchange part is formed.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to improving the structure and performance of a heat radiator by effectively utilizing a heat pipe.

In particular, the present invention consists of three parts: a heat receiving metal block, a heat pipe inserted into the block, and a heat exchange part whose main component is the heat radiating part of the heat pipe,
The present invention relates to an improvement in the structure and performance of a heat pipe type radiator that transfers the amount of heat absorbed from the heat receiving plane of a heat receiving metal block to a heat exchange section and radiates the heat from the heat exchange section.

Further, the equipment targeted by the heat sink is mainly equipment applying semiconductor electronic components, and the heating element targeted is mainly semiconductor elements.

←) Conventional technology The structure and performance of a heat sink with this structure has been improved by the structure of a heat receiving metal block that efficiently absorbs the heat of the heating element and allows it to be efficiently absorbed by the heat absorption part of the heat pipe. The first improvement is to improve the heat pipe, which is used to efficiently transfer the amount of heat to the heat radiating part with faster response. These three points, the third one being improvement of the structure of the heat exchange section, are the key points for improvement, and many efforts have been made in the past for this improvement. However, the rapid development of recent technology has made many heating elements smaller and lighter, and at the same time has increased their heat generating capacity. In many devices, the heat receiving capacity of the heat receiving block and the performance of the heat pipe are reaching their limits within a given space factor and permissible weight range. Particularly in heat exchange parts, as the heat dissipation capacity increases, the area required for the heat dissipation fins increases rapidly, and heat dissipation by the fins has the fateful property that the fin efficiency decreases as the fin volume increases. The increase in efficiency and weight has become a major barrier to miniaturization of equipment. A typical example of such a heat sink is a heat sink for power semiconductor devices.

FIG. 13 and FIG. 14 show a heat pipe type radiator for a flat thyristor for electric power. In the figure, the lfl heat receiving gold eye block is mainly made of pure copper in order to lower the resistance value. 2 is a heat pipe for heat transfer, and since high reliability and high performance are required, a pure water working fluid and a pure copper container are used. Since long-term corrosion resistance is required in the Aij heat exchange section, pure copper fins are generally used as the heat dissipation means. Heat pipe 2 is heat receiving metal block 1
It is thermally connected to the block through an insertion hole 4 provided in the block. Since the heatsink is required to have a low thermal resistance value of 0.015 to 0.02 degrees per two heatsinks sandwiching one element, that is, a relative value of 0.015 to 0.02 degrees, the heat pipe and the block are very popular. Since the occurrence of contact thermal resistance is not allowed, use Pb for insertion.
-8n Adhesion using solder is also used. As shown in FIG. 13, a group of flat thyristor elements and a group of radiators are generally used as a heat radiating stuff in a laminated structure.

Typically, forced cooling air is supplied to the heat exchange section in the direction of the arrow. Ten years ago, the mainstream of thyristor elements was around 400W per element, but the capacity has increased year by year, and in recent years the mainstream has been IKWfi per element.
．． Depending on the performance improvement of 5KW and 2KW coolers, they are on the verge of being put into practical use. As the capacitance of devices increases, the thermal resistance value required for the heatsink is 0.025~
While the conventional maximum level was about 0.02°C/W, recently there has been a demand for high-performance products with a relative value of 0.015 to 0.01°C β. For thyristor heatsink,
As shown in FIG. 13, the measurement is carried out by holding one element between two heat sinks (pair), so the measured values are shown below as paired values.

On the other hand, since the thickness of the element does not increase in size, its diameter is about 60 to 80 cm, and its thickness does not exceed the range of 15 to 30 m5, so the heat absorption performance of the heat receiving metal block is approaching its limit. be. As a measure to increase the capacity, the size of the heat receiving metal block and the heat absorbing part of the inserted heat pipe have been increased. In FIG. 14, only the heat receiving portion of the heat pipe is enlarged to increase the heat receiving capacity. However, such a heat sink can be used under pressure with several units in order to lower the contact thermal resistance between the element and the heat receiving plane, and this also limits the increase in the diameter of the heat pipe. 1st
In the example shown in Figure 4, when element 5 has a diameter of 80m+, the diameter a of the insertion hole (heat absorbing part of the heat pipe) is generally around 40m+, but from the figure, this is mostly the case. It turns out that there are limits. That is, it is clear that when the length is greater than 40 m, the amount of #I received from the element surface by the heat pipes on both rows of the three heat pipes decreases, resulting in a decrease in efficiency. Also, the maximum number of insertion holes with a diameter of 40 m is three. If the number of heat pipes is increased to four or more, the amount of heat received by the outer heat pipes will be greatly reduced, and the efficiency of the radiator will be reduced. Fig. 15 is a bottom view of the heat receiving metal block 1 in Fig. 14, and when the diameter of the insertion hole 4 is around 40 m, the distance from the heat receiving plane of the block to the outer periphery of the insertion hole is 10 to 13 points. It is customary to take This is to withstand pressure during use, and if the heat receiving block is made of soft pure copper or soft aluminum, if the distance is made any smaller, the heat pipe may buckle. Due to such a distance, the thermal resistance value of heat passage from the heat receiving plane to the heat pipe is 0.01° C. β1. The total thermal resistance of the radiator, which is the sum of the thermal resistance of the heat receiving metal block, the heat pipe thermal resistance, and the heat exchanger thermal resistance, is 0.02°C/W (0.04°C/1 piece). The current situation where W) is required is 0.01 just for the heat passing through the heat receiving block.
℃β(2) It must be considered that the occurrence of thermal resistance is close to the limit. If the diameter of the heat pipe heat receiving part is 50 ports,
In order to increase the distance to 60 miles, it is necessary to increase the distance between the heat receiving plane of the heat receiving metal block and the surface of the heat receiving part of the heat pipe or the outer periphery of the insertion hole by several points, which further increases the thermal resistance of the heat receiving metal block. In proportion to this, the heat absorption performance from the heat receiving plane cannot be improved, resulting in an extremely unreasonable result. In order to reduce the distance from the heat receiving plane to the heat pipe surface and further reduce the overall thermal resistance of the heat pipe, the diameter of each heat pipe is reduced to increase the withstand pressure and the number of heat pipes is also increased. be. FIG. 16 is an example of this, and is a view seen from the bottom side, similar to FIG. 15. However, in this case as well, the distance from the heat-receiving surface is only slightly shortened, and the number of wires is limited to about six. This depends on constraints arising from the position relative to the fins 3. As can be seen from FIG. 13, when the thickness of the element 5 is 15 to 30 mm, if the width of the fin is made 15 to 20 wa or more larger than the width of the heat receiving metal block 1, contact with adjacent fins or discharge may occur. It becomes unusable. Therefore, if the heat pipe is placed too close to the heat-receiving plane, the fin height at the fin portion becomes too small, causing problems in terms of heat transfer performance on the fin surface. Therefore, the distance 111 from the heat receiving plane needs to be the same as if in FIG. Similarly, in the fin section, the FA between the heat pipes is at least 15~2011II! Because of the above requirements, it is necessary to provide insertion hole gaps of 15 to 20 fins in both the row direction and the step direction in the heat receiving metal block as well. In FIG. 16, if the heat pipe diameters are arranged in 16 orders and the element diameters are set to 80 degrees, the number of heat pipes required to receive heat efficiently is 3 (pieces) x 2 (columns), or 6 in total, as shown in the figure.

When the diameter of the heat pipes is 20 m, the length of one row of three heat pipes is 100 degrees, and they can be placed barely close to the heat receiving plane. Even when the diameter of the heat pipes is 112 m, the length of one row of three heat pipes is 76 m, so it is not possible to have 4 (pieces) x 2 (rows). In the end, in this case, the number of heat vibro tubes is 16 to 20 tm in diameter, and it can be seen that the distance between the heat receiving plane and the heat pipe surface is hardly improved. The improvement in heat pipe capacity in this case is as follows. The capacity of the heat pipe is proportional to the inner area of the container. In the case of Figure 15, the heat pipe diameter is 40 m.

When the pipe thickness is 1 vtx and the effective length is 80 m, the total internal area is (40-2)
m, r? becomes. In the case of FIG. 16, the heat exchange section uses a 25 W CD with a diameter of 20 W at the insertion section, and when the pipe thickness is 1 W + effective length of 180 m, the internal area of the heat absorption section is as follows.

(25-2) XπX80
56 only improved. However, since the diameter of the insertion part was increased by 5 m, the distance u from the heat receiving plane to the heat pipe surface
Since it can be improved to 8 m to 10 m, the heat passage resistance of the heat receiving metal block can also be improved by about 20 m. However, this level of improvement will have no effect on achieving the capabilities required by the industry.

The performance of the heat exchanger in current radiators is also a major problem. Particularly in the case of power thyristor heat sinks, the width of the fins is limited to an extremely narrow range as described above. Also, it is impossible to make the length sufficiently long. As can be seen from Figure 14, it is possible to make the forced cooling air longer in the flow direction, but since the heat pipe is concentrated close to the top of the heat receiving part, the fin efficiency deteriorates even if the fin ends are made longer. The thyristor element diameter is 8 (in a 1 m heatsink, the conventional fin length is gtrxso~20).
0m is the limit, and making it longer than that is completely meaningless. Therefore, the heat dissipation area per fin is extremely small, so a large-capacity heatsink such as IKW usually requires 200 or more fins, and if the fin pitch is 4s, the height of the heat exchanger is 1jsoo. Requires more than a sieve. The volume and weight of the heat exchange section in a thyristor radiator are major problems, and if left as they are, there is a risk that this will hinder the future development of power thyristors.

The problem of volume and weight of the heat exchanger due to fin heat radiation is also an important problem in cases other than thyristor heat radiators. In the case of fin heat dissipation, the heat transfer coefficient of the cooling air is a practical wind speed of 2 to 3 [
m/@] is around 30 (W/m'c). Therefore, if the heat dissipation capacity is the same, the same volumetric weight is required for cooling other equipment. Furthermore, in the case of natural air cooling heat dissipation, the heat transfer coefficient of the fins F'i5 [W/y] decreases around 100%, and the fin pitch needs to be around 110 -, so the fin surface area is smaller than that of forced air cooling with the same capacity. It requires 6 times the area and 1j15 times the volume, and is a more important problem to be solved than forced cooling.

The problems with heat sinks for cooling power thyristors have been described above, but many of the heat pipe type heat sinks for power semiconductor devices have similar problems. In other words, due to the rapid development of semiconductor devices, small and powerful power transistors have been put into practical use.Compared to power thyristors, these devices have a smaller amount of power and a smaller heat receiving block, but the area of the heat receiving plane is smaller. The volume given to the heat dissipating fin group is small, and the ambient temperature is high.As a result, the required performance for the heat dissipator is extremely strict, and the thermal resistance value is o, o.
There are many cases where high performance such as <'cβ] is required.

Another problem common to heat pipe type radiators is that as the load heat capacity increases, the heat receiving block becomes larger, its heat capacity becomes excessive, and the thermal response of the radiator as a whole decreases despite the improvement in the heat radiator's heat dissipation capacity. One of the problems is that it is becoming more and more common.

(c) Problems to be solved by the invention In response to strict demands from industry, the heat pipe type heat sink according to the present invention has achieved an extremely low thermal resistance value that was previously thought to be impossible. The problems to be solved in order to provide a high-performance heatsink exhibiting fast thermal response are as follows.

(&) Fundamental improvements to the block structure to significantly reduce the flow-through thermal resistance for heat to pass through the heat-receiving metal block, which has currently reached its limit due to the various constraints mentioned above.

(b) Improvement of the block structure to take advantage of the heat pipe's excellent thermal response performance without being affected by the increase in size of the heat receiving metal block.

(c) A novel method for significantly lowering the thermal resistance of heat pipes.

(d) Fundamental improvements in the structure of the heat exchanger that can reduce thermal resistance despite its small volume.

(e) At the same time, as an incidental problem to be solved, in the case of extremely high-performance heat sinks, it is necessary to have means to protect the heat exchanger from contamination caused by dust, which has a large effect even if it is small, and corrosion caused by W surroundings.

2) Means for solving the problem As mentioned in the section of the prior art, the performance and structure of the radiator consisting of the heat receiving block, heat pipe, and heat exchanger are close to their limits, but it is difficult to reach their limits. The biggest factor was securing the fin area, and the second factor was maintaining pressure resistance against the pressure applied during use. The solution to the problem in the radiator structure according to the present invention is "heat radiation that does not rely solely on fins"
The first basic idea is ``high performance that does not rely on increasing the diameter of the heat pipe.'' The second basic idea is ``high performance in receiving heat by increasing the number of small diameter heat pipes.'' We have arrived at a new structure as a means.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, means for solving problems for improving the performance of a heat radiator provided in a heat pipe type radiator according to the present invention will be explained with reference to the drawings.

FIG. 1 shows the basic structure of a heat pipe type radiator according to the present invention, and FIGS. 8, 9, and 10 show the basic structure of the heat receiving metal block in FIG. 1. In the figure, 1 is a heat receiving metal block, and 2 is a group of small diameter heat pipes. Each heat pipe is shown only by its center line to make the drawing easier to read. Reference numeral 5 denotes a power thyristor element which is brought into pressure contact with the heat-receiving plane of the heat-receiving metal block 1, and the two are connected electrically and thermally with an extremely low contact thermal resistance that cannot be measured. . Heat receiving metal block 1
It is formed into a prismatic solid shape with the heat receiving plane as the bottom. The prism is not limited to a square prism as shown in Figure 1, but may be a pentagonal prism or a hexagonal prism, and is not limited to a regular polygonal prism, and the length of the bottom corner side can be set to a desired length. I can do it. Furthermore, other irregular shapes processed using this as the basic original shape may be used.

FIG. 8 is a front view of the heat-receiving metal block shown in FIG. 1, that is, in the case of a square prism, as seen from the heat-receiving plane side. Figure 9 is a side view of Figure 8 and a plan view of Figure 1() 1r. Insertion holes 4 for inserting heat absorbing portions of heat pipes are drilled into the block from a plurality of side surfaces of the block parallel to the heat receiving XP plane and parallel to each other.

When viewed from the heat receiving plane side, the insertion holes drilled from one side always intersect with the insertion holes drilled from the other side, and when viewed from the side, they never intersect. They are arranged so that they do not cross each other. The insertion hole may be a through hole or a non-through hole. In Fig. 1, groups of insertion holes are drilled from the upper and right side surfaces of the heat receiving metal block 1, and 64 holes are drilled on both sides with 4 rows and 8 rows of insertion holes on each side. There is. The heat absorbing portions of heat pipes are closely inserted into each of the insertion hole groups 4 of the heat receiving metal block 1, and the heat transfer portions of these heat pipes may be bent as appropriate or left straight. Accordingly, the heat radiating parts of those heat pipes are introduced into predetermined positions of the heat exchange part of the radiator, and are arranged in a predetermined row of tube groups to form the heat exchange part. There is. In FIG. 1, the heat pipe group 2-2 on the right side is bent upward, and the heat pipe group 2-1 on the upper side remains straight and is fully aligned and extended, and is surrounded by the wind tunnel side plate 7. It is located inside the heat exchange section. FIG. 12 shows the arrangement of heat pipe groups in the wind tunnel. The figure shows a heat exchange section that relies on natural convection, which will be described later, so the 2-1 group and 2-2 group are introduced into different wind tunnel side plates, and the upper and lower partition plates 8 are used to separate the heat exchanger from the air heated in the lower wind tunnel. Prevents convective wind from entering the upper wind tunnel. This is an example of heat dissipation by forced convection wind indicated by the arrow on the side of the heat exchange section in FIG. 1. In this case, the two wind tunnel side plates in FIG. 12 are connected and integrated, making eight partition plates unnecessary. In the figure, the heat pipes in the wind tunnel are arranged in a staggered arrangement, but the arrangement may be in a grid pattern or in some other arrangement.

As a basic condition of the heat radiator according to the present invention, the heat radiating section of the small diameter heat pipe group in the heat exchange section is made of unfinned metal tubes or loaf-in tubes in order to obtain a high heat transfer coefficient similar to that of a multi-tube heat exchanger. It is formed accordingly. Since the fins of the loaf-in tube have the same outer diameter as the outer diameter of the non-finned portion, turbulent flow within the wind tunnel is not hindered.

Even if it is unavoidable to insert fins due to insufficient heat transfer area, only small-area tubular thin fins with a fin height of 6W or less are allowed as the basic structure of the present invention. The fin height of 6w is the limit fin height that shortens the shortest distance between the heat receiving plane and the heat pipe and significantly reduces the thermal resistance of the heat receiving metal block.

If ordinary plate fins are inserted, the effect of the heat sink of the present invention, which aims to utilize the turbulence effect generated by the tube group, will be lost due to its rectifying effect, and the heat pipe arrangement pitch In the case of annular individual fins whose diameter is less than 2.5 times the heat pipe diameter, the tube group effect is not lost.

Although not shown in the drawings, the heat receiving metal block 1 in FIGS. 1, 8, 9, and 10 may be a laminated structure consisting of a large number of flat metal blocks. In this case, it is desirable that the division be performed along a plane parallel to the heat receiving plane, and that each row of insertion holes should be divided. Also, each flat plate type Kinki block has an external shape.

It is desirable that all the insertion holes have the same shape.

When constructed in this way, each flat metal block can be simultaneously extruded as a long material including the insertion holes using the same extrusion die. The heat-receiving metal block according to the present invention can be completed by cutting this extruded material and stacking them together so that the insertion holes intersect with each other, thereby significantly reducing processing costs.

Furthermore, completing the insertion and connection of the heat pipe group before stacking makes the insertion and connection work easier. The laminating means may be adhesive, soldering, mechanical combination, or a combination thereof.

(e) Effect) The thermal resistance of the heat receiving metal block can be reduced to 1/4 to 1710 or less.

Since the heat pipe and insertion hole have been significantly reduced in diameter, the pressure resistance has been significantly strengthened. Furthermore, there is no need to consider the efficiency of the radiation fins at all. Therefore, the distance from the heat receiving surface to the insertion hole path can be made sufficiently small, and the center distance between the insertion holes can also be greatly reduced. In Fig. 1 and Figs. 8 to 10, when the inner diameter of the insertion hole is set to 10, the distance of the insertion hole path from the heat receiving plane is ij1, 5w.
It is possible to reduce T7) to about -3m, and the center distance between the insertion holes can be reduced to about 13m+. In this case, in the case of a regular hexahedral block with a side of 104 m+ as shown in the figure, 64 insertion holes in 8 rows and 8 stages can be drilled.

A heat receiving block with a heat receiving plane having an area of 104 m x 104 +++ m is suitable for a Sirisk element with a diameter of 80 pieces,
For this reason, in heat receiving blocks of conventional construction, the diameters of the heat pipes and insertion holes are usually 40 degrees, and it is customary to use one with two holes in one row and two stages. In this case, the distance from the heat receiving plane to the insertion hole path is 13■, and the center distance between insertion holes is 1j6
011Ill was the standard.

Since the flow-through thermal resistance is proportional to the distance from the heat-receiving plane, the thermal resistance of the first row self-propelled near the heat-receiving plane of the heat-receiving block according to the present invention illustrated in FIG. It will be approximately 1/10. Furthermore, since the thermal resistance of the heat receiving block according to the present invention is a composite thermal resistance of the respective thermal resistances of the first to fourth columns, the total thermal resistance can be reduced to about 1/20 compared to the conventional one. is assumed.

The actual measurements are for a heat pipe 2 with a diameter of 40cm with a conventional structure.
The thermal resistance value of a pure copper block with a heat-receiving plane of 100 mm x 100 m+ with a book inserted is 0 in terms of the relative value when the element diameter is 80 m.
A value of 0.008 (°C/W) was obtained. Similarly, a heat receiving block in which four heat vibros of the present invention having a diameter of 10 m were inserted had a heat resistance value so small that it was impossible to read the measured values. The estimated value is 0.0 in contrast.
It is estimated that the temperature is below 0.004C°C/W). In the present invention, in order to compensate for the lack of heat dissipation area, when installing fins on the heat pipe, the fin height is set to 8 tt's.
Limited to 6 m or less.

In the case where the fin height is 6 mm, if the shortest distance between the heat receiving plane and the heat pipe is set to 1.5 to 3 mm, the fins will protrude from the heat receiving plane by 3 to 4.5 mm.

This is a limit to prevent discharge from occurring between the fins of adjacent heat sinks.

(b) Improvement in thermal response The heat receiving block of the conventional structure has a long distance from the heat receiving plane and a large gap between the heat pipes, and as the heat receiving block becomes larger, the thermal response deteriorates. However, in the case of the heat receiving block of the radiator according to the present invention, the distance between the heat pipe and the heat receiving plane is 1
．． It is only 5~3m+, and the gap between the heat pipes is 2~
Since the amount of heat absorbed on the heat-receiving plane is only three degrees, the amount of heat absorbed on the heat-receiving plane is first absorbed by the first row of heat pipes close to the heat-receiving plane before being transmitted inside the heat-receiving block, so the thermal response characteristics of the radiator The thermal response is close to that of a single heat pipe, and the thermal response time is at least 1/10.

Furthermore, since the heat pipe groups within the block are close to each other between intersections tf, the entire block can be made uniform in a short time, and the thermal response time can be shortened.

(c) The heat transfer characteristics of the heat pipe are significantly improved.

Thermal resistance of the heat pipe is improved in proportion to the inner area of the heat absorbing section and the heat dissipating section of the container. Therefore, when the lengths are the same, the improvement is proportional to the inner diameter of the container. As an example, as in the case of the heat receiving block, a case where two heat pipes with an outer diameter of 40 mm are used and a case where four heat vibros with an outer diameter of 10 mm are used will be compared.

In both cases, the container wall thickness is 0.8 trwn, the length of the heat absorbing section is 100 mm, and the heat dissipating section is 250 mm.

The performance ratio of both is (40-0, 8X21 X2=(10-
0.8X 2 ) X 64 .

That is, 76.8=537.6, and the performance is improved seven times.

The actual measured value of the thermal resistance of a heat pipe with a diameter of 40vts and a length of 350m is 0□023 ["CI]" for one heat pipe, so the value for each two heat pipes is 0.0115 ('C seat).
．． It becomes 0058 ('C/W).

Therefore, in the case of diameter 10 + o + 84 pieces, it becomes 0.00164 (℃β) per 1-j64 pieces, and the paired value is 0.0008
It should be C℃β.

In addition, the actual value of the thermal resistance of a heat pipe with a diameter of 10 mm and a length of 300 tubes was separately measured as ijo, 11 ('Cβ). Therefore, t-j O, 00017 per 64 pieces.
[℃β], and the relative value is 0.00086 C℃β].

Therefore, the estimated value from the area ratio is almost the same as the actual measured value, and the total thermal resistance of the heat pipe shown in Figure 1 using 64 small diameter (10 m) heat pipes ij O,0008 to 0.0009 ('C
/W) (vs. value), which indicates a significant improvement. In the example shown in Fig. 1, the example is 10m x 64 pieces of water, but if the heat receiving area is the same, 8m x 100 pieces, 6cm x 169 pieces,
It is possible to make it 5 m x 256 lines, etc., and there is room for further significant improvement.

The effect that the heat pipe groups intersect within the heat receiving metal block is one of the important functions of the heat pipe type radiator according to the present invention. A conventional heat pipe type radiator F'il (a number of heat pipes arranged in parallel in one direction).In this case, each heat vibrator has a different distance from the heat receiving plane, The amount of heat received by each pipe was different.Also, the heat transfer direction of the heat pipes was linear, so each heat pipe's ability was rarely matched4.Also, the heat receiving plane was usually Since the contact plane with the plane of the semiconductor element is a circular plane, the amount of heat received by the outer heat pipe of several heat pipes is particularly small. The groups intersect each other in close proximity, and the intersections are in several layers.

Each heat pipe group not only functions to transfer the amount of heat received by each heat pipe to the heat radiating section, but also functions to equally distribute the amount of heat received among the heat pipes of the adjacent heat pipe group. In other words, all the heat pipes that are inserted and connected receive heat I from each other.
IF'4r: All heat pipes receive heat evenly by sharing and mutually assisting each other, and evenly exhibit heat transfer ability. Also, due to this action, the heat of the heat-receiving metal block is uniformized over its entire volume. Due to these effects, the entire length of the inserted heat pipes is effectively utilized, and the entire length of the inserted heat pipes is most effectively utilized. As a result, the performance of the heat pipe of the radiator according to the present invention is significantly improved.

(d) The heat dissipation ability of the heat exchange section is significantly improved.

The temperature difference between the heat exchange capacity QV1 of the heat exchanger and the fin surface temperature (or heat pipe surface temperature) is Δt('
), and the fin surface area (or heat no(eve area)) is S
a(m'), the heat transfer coefficient between the heat transfer surface and the surrounding air is α(W/
-h'c), it is determined by these values. In that case, the reciprocal of the capacity, that is, the thermal resistance, is Ra (°C/
W), we have the following relationship.

Ra -1('c/w) Q-axSxc[W]--
By comparing the temperature under WX, that is, the ambient tm degrees, and Δt, assuming a constant value, it is possible to determine the superiority or inferiority of the heat exchange performance of the heat exchange section.

On the other hand, it is well known that when comparing the value of α between a flat plate placed parallel to the flow (fin plane) and a cylinder placed perpendicular to the flow (heat pipe), the cylinder is larger. Possible reasons for this include that turbulence is less likely to occur on a flat plate, and that Δt becomes smaller in the downstream OIIl on the plate surface depending on the amount of heat received on the upstream side. It is also well known that the α value of a cylinder that falls perpendicular to the flow increases as the diameter decreases.
Furthermore, it is also known that when there are many cylinders arranged perpendicular to the flow, and the appropriate arrangement such as staggered arrangement or grid arrangement is made, the thermal conductivity α increases several times. It is also known that the value of the heat transfer coefficient α increases rapidly as the flow rate of the heat exchange fluid increases.

On the other hand, the surface area of a cylinder (heat pipe) placed in a flow can be increased within the same volume as the number of smaller diameters increases.

The present invention combines these effects and utilizes the synergistic effect, and as can be seen from Figure 1, a large number of heat dissipation parts of small diameter heat pipes are arranged in the heat exchange part, and the heat transfer coefficient is greatly increased. α and the significantly increased surface area S form a heat exchange section with low thermal resistance, and are intended to simplify and improve the performance of heat pipe type heat sinks, which traditionally relied too much on fin groups. be. As an example, a plate-fin type thyristor heat radiator using two heat pipes with a heat absorbing part diameter of 40 m and a heat radiating part diameter of 32 m, which are most frequently used as a power thyristor heat radiator, is used as a heat pipe for a heat radiator according to the present invention with a diameter of 10 m. Let's compare the case of using 64 pieces and the case of using 169 pieces of 6m diameter.

Medium Surface area magnification nl of the heat dissipation part of the present invention (32ttan, relative to the surface area of two heat pipes) φ6 gourd n1=6”X, 15.8 times in 1LJL 32π×
2 (II) Surface area magnification nf of plate fin type heat dissipation part
(For a heat pipe surface area of 32 m + 2 lengths of 250 wm) Fin length: 200 + w, Width: 75 m, Fin pitch: 2 m.

Number of fins: 125 Fin surface area (200X75-322XiX2)X12
5X2=3347876Cmm”) Heat pipe surface area 32×π×250×2=50265.5 [mrr?]j
1710 magnification nf=i',' 4-, +166.6
times 11iD Plate fin heat transfer coefficient αf (forced convection) However, Representative temperature t-45℃ Δt=io℃ Fin height t=o, 2m Kinematic viscosity of air at 45℃ C45=18.025X
10~%] Thermal conductivity of 45℃ nickel air λ4Is=o
, 02 a 7 (Kca 1/mh℃) Prandtl number of air at 45℃ Pr=0.71 Air flow rate n=3 (m/S) Pohlhausen's method Num=0.664x
αf is determined based on PrxRem+.

αf=NumX”””12.81 (Kcal/m”
Heat transfer coefficient αHP (forced convection of tube group) of the heat dissipation section of the present invention Since the heat dissipation section of the present invention has no fins and has a small pressure drop, it is possible to apply forced convection air using a fan under the same conditions as 0iil.
The speed is increased to 5 (/S).

Using the Grimson method and H1lp6rt method, the number of Certs is calculated and αHP is determined.

Num-0,575xRem'L'6'Xp,k xQ
・98φl-αHp=97.82 (Kcal/m'
h℃)φ6wn aHp=122.85(Kcal/m
'h'c) M Multiplier of the capacity of the heat exchange section of the present invention with respect to the capacity of the plate fin heat exchange section n .6 Even if the heat exchange section according to the present invention has no fins at all, in the case of the embodiment shown in FIG. 1, the efficiency is about 15% higher with 64 heat pipes with a diameter of 10 m+, and 169 with a heat pipe diameter of 8 m
The book shows that 128 people are highly efficient. The respective thermal resistance values are as follows. (However = o, oos75C℃/W)
(Idanshi Bunga Nao) 6 Xo, 86÷2 φ6tm RI″″″122, 85X6gX169x
250) 4ff=o, oo44C'C/tov] (1st value versus value) This example is compared in the case of forced convection heat conduction, but in the case of natural convection heat conduction, the natural convection wind speed inside the fin is 0. 2
Cm/S'J Wind speed in the heat exchange section according to the present invention: 0.6 m/8
(Taking into account the fact that the chimney effect is easy to use), the result of the trial calculation was that the capacity would be approximately doubled.

(e) Corrosion prevention measures become easier.

The heat exchange part of the radiator according to the present invention has no fins at all, or
Since it is configured with a heat pipe having extremely low height fins for heat dissipation, it is possible to easily perform batch plating and batch painting using the dipping method. It is also possible to electroplate the heat pipe wood assembly.

In the case of plate fins, it is impossible to apply anti-corrosion coating after inserting the fins, so it is necessary to apply anti-corrosion plating to each fin before assembling the fins. If the paint was resistant to adhesion, the heat resistance would increase after the fins were inserted, making it impractical to apply anti-corrosion coating before mounting.

(f) The old method of using adhesives to connect the insertion hole and the heat pipe heat absorbing portion is no longer necessary.

The contact area of the 1"° insertion part is extremely wide due to the large number of insertions.The thermal resistance of the contact part of the conventional 40cm diameter 2-piece insertion is reduced, making the conventional solder bonding process obsolete. However, it is possible to replace the adhesive with a thermally conductive adhesive.In Figure 1, the thermal conductivity of the thermally conductive adhesive is 0,9 [W/
mlc) When the inner diameter of the binding insertion hole is 10.15 [fin] and the outer diameter of the binding heat pipe is 1O [■], the thermal resistance value depending on the adhesive is calculated as 0.0004 [℃/W] vs. The value is 0002 ('C/S), which has almost no effect on the performance of the heatsink.This is extremely important in the case of the heatsink of the present invention, which requires the insertion of several tens of heat pipes. However, it was difficult to put the heat pipe type heat radiator of the present invention into practical use when it required "adhesive adhesion" which is a difficult work with poor workability, but it has been made practical by using an adhesive. It was possible to do so.

(g) Electrical insulation between the heat exchange section and the heat receiving block becomes possible.

When a heat pipe type radiator is used to cool a semiconductor device, it is often desired to provide electrical insulation between the heat exchange section and the heat receiving block. In particular, in the case of electric power silices, the heat radiating parts are very close to each other, so there is a risk of electrical discharge occurring between the fin groups, and there has been a desire for a radiator that does not create a potential difference between the heat exchange parts. For this reason, various proposals have been made for insulated heat nozzles.Most of them have an intermediate part made of electrically insulating material between the heat receiving part and the heat dissipating part of the container, and an electrically insulating material is used as the working fluid. Structural 1: It is complicated, expensive, and has low performance, so it has not been put into practical use as a high-performance heat sink.Also, we have proposed a method in which the heat receiving part of the heat pipe is coated with insulation. However, in the case of the heat sink according to the present invention, the contact area with the heat receiving block is extremely wide. By using a material with high
In order to improve the reliability of gas insulation, a highly reliable intervening film such as a baked polyimide thin film may be used in conjunction with the adhesive. As an example, in Fig. 1, the inner diameter of the insertion hole is 10.2 m, the thickness of the polyimide thin film layer is 0.025 rpm, and the thickness of the thermally conductive adhesive layer is 0.0 m.
It is the heat of the bonded part when the heat conductivity of the thermally conductive adhesive is o, 9 (W/m℃) and the relative value is o, ooo5c°C/W), and there is no practical problem at all.

(In) Maintenance inspection and cleaning are extremely easy.

Compared to the common plate fin structure, it is easier to disassemble and reassemble, and it is convenient for maintenance and inspection. In addition, compared to plate fins, the turbulent flow makes it less resistant to dust adhesion, and dust can be easily removed by spraying water vapor or compressed air without decomposition.

(1) It can be applied to both natural convection and forced convection, and the refrigerant fluid can be either liquid cooling or air cooling.

Since the heat exchange part of the heat pipe type radiator according to the present invention is mainly composed of heat pipes formed of finless tubes or loaf-in tubes, the fluid resistance is small, so natural convection heat radiation and forced convection heat radiation are possible. It can be applied regardless of whether it is liquid-cooled heat radiation or air-cooled heat radiation.

In particular, since it is possible to electrically insulate between the heat receiving block and the heat exchange section, the heat exchange section can be safely water-cooled, even when cooling a heating element where a high potential is applied to the heat receiving block. Significant downsizing becomes possible.

(f) Embodiment 1 Embodiment 1 FIG. 1 μ This is a basic embodiment of a heat pipe type radiator according to the present invention. Its detailed structure is as described above, but in this embodiment it is used only for heat dissipation by forced convection. When used for natural convection, the heat dissipation portion of each heat pipe is parallel to the flow, and the cooling efficiency of each heat pipe is significantly reduced, and the turbulent flow effect due to the tube group is also lost, making it unusable.

As a refrigerant fluid, it is also applied to keg, cold, and air-cooled sidewalls.

The orientation of the heat pipe within the heat exchanger is not necessarily limited to vertical orientation.

Second Embodiment FIG. 2 shows a second embodiment of the heat pipe radiator according to the present invention. In the second embodiment, a hexagonal pillar block is used as the heat receiving metal block.

Insertion holes are provided on all sides other than the bottom side and the surface where the power terminal 6 is attached. All of them are located in the heat exchange section at the top of the block. This embodiment is particularly effective when increasing the number of heat pipes. Furthermore, when the number of heat pipes is kept constant, the arrangement density of the heat nozzles in the heat exchange section can be lowered, so by inserting annular fins into a predetermined part of the heat/quiz, the present invention can be used. It is possible to combine the structure with the conventional annular fin structure, and it is also possible to expand the heat transfer area. In this embodiment, if the side heat tube group 2-2 is omitted, the remaining heat
, 2-3, 2-4 d16 right angle bend kfl) No E < The structure is easy to bend.

Third Embodiment If a heat exchange part is provided on one side of the heat receiving block in Fig. 3.
! This is a third example. The heat nozzle group is maintained almost horizontally in the wind tunnel. If the heat dissipation part is small and has several hundred parts, horizontal is fine, but if it is longer than that, it is necessary to maintain a good working fluid flow inside the antenna. The thermal resistance of the heat dissipation part can be reduced by adopting an inclined position as shown in the figure.The figure shows a case where heat is applied to natural convection heat dissipation, and the natural convection shown by the arrow flows from the bottom to the top.Forced convection For heat dissipation, the flow of refrigerant fluid may be horizontal or vertical.

FIG. 11 shows the wind tunnel side plate 7 in the third embodiment, and shows the arrangement of the heat pipes 2. In the case of natural convection heat dissipation, the upper side heat pipe group 2-1 and the side heat pipe group 2-21 in Fig. 3 are divided into upper side plates 7-1, respectively.
and the lower side plate 7-2, and an upper and lower partition plate 8 is provided between both groups, so that the heat medium fluid heated by the 2-2 heat pipe group is
Preventing low-temperature fluid from flowing into the -1 heat pipe group and allowing low-temperature fluid to flow into both groups can improve heat exchange efficiency.

Fourth Embodiment FIG. 4 shows a wX4 embodiment, in which the heat receiving metal block 1 in the embodiment of FIG. 3 is formed into a pentagonal prism.

5th ij! Embodiment and Sixth Embodiment FIGS. 5 and 6 show the fifth and sixth embodiments of the heat pipe type radiator according to the present invention, respectively. This applies only to forced convection heat dissipation.
In the figure, the heat exchange part is cut out on the side, so it can also be applied to the natural convection side and forced convection side. As a characteristic of the heat pipe type heat radiator, the fifth embodiment in which the heat radiating portion of the heat pipe is vertically provided exhibits higher heat radiating ability.

In both embodiments, heat pipes extending from a plurality of side surfaces are integrated and arranged in a cross section that is equal to or slightly wider than the heat receiving plane. The arrangement state is shown in the heat pipe group 2 inserted into the wind tunnel side plate 7 in FIG. In this case, the heat pipe array is arranged so that the center distance is 1.2 to 1.6 times the heat pipe diameter both vertically and horizontally, so that the heat transfer coefficient reaches the maximum due to the turbulent flow effect of the tube group during forced convection. They are arranged in basic order, staggered arrangement, or their applied arrangement. In this embodiment, compared to the conventional plate fin structure, the volume of the heat exchange section can be made smaller, and higher heat exchange performance can be achieved.

(e) The trial calculation of αHP in section d was calculated based on Example 1 and 5.

Ig7 Embodiment Figure 7 shows the seventh embodiment of the heat pipe type radiator according to the present invention, in which both sides where the insertion holes are drilled form roof-shaped 45-way slopes, and forced cooling is achieved. This is the simplest embodiment for practical use. The bending process of the heat pipe VsB only needs to be performed at an obtuse angle of 135 degrees, and the process is the easiest. In addition, the heat dissipation parts of each heat pipe are all vertical, and there are no heat pipes that are bent at right angles, and there is no bending process to make the path to the heat dissipation part a long distance. Since the reflux of the liquid and the movement of the working liquid vapor are easy, this example is the one that can easily exhibit the highest performance among the examples. However, if this embodiment is rotated 90 degrees clockwise as shown in Figure 7 and the heat exchange section is held horizontally, the position of the heat receiving section of the heat pipe group 2-2 will be higher than the heat dissipating section, resulting in a top-heat state, which will result in poor performance. Most will be lost. Therefore, this embodiment cannot be used for natural convection heat dissipation or horizontal forced convection heat dissipation. However, when the heat receiving plane is held horizontally, the heat exchange section is held horizontally and no top heating occurs, so the structure of the present invention can be applied to both natural convection heat radiation and forced convection heat radiation.

The seventh embodiment described above is an applied example only in terms of the structure of the heat pipe type radiator according to the present invention, and includes detailed embodiments of each example that can only be implemented by the heat pipe type radiator according to the present invention. Combining structures results in even more applications being obtained. Detailed examples will be described below.

Lotus) The radiator according to the present invention, wherein the thin tubes according to the present invention have a diameter of 12 mm or less, and the number of tubes is at least 12 or more.

B. In implementing the present invention, it is necessary to bend a large number of heat pipes and arrange them at predetermined positions in the heat exchange section. Therefore, there are two stages of bending in the pre-assembly process: first bending is the bending of the container before it is formed into a heat pipe, and second bending is manual alignment during assembly. In order to implement using a large number of heat pipes, both of the two stages of bending must be easy. We have found from experience that the diameter range of 10 W or less is within the diameter range in which the heat pipe in the heat sink according to the present invention can be bent very easily in both the primary and secondary stages, and although there are some difficulties, it is practical. It has been concluded that the limit diameter that can be practically implemented is 12+m+.

The heat exchange section of the radiator according to the present invention takes advantage of the synergistic effect of improving the heat transfer coefficient by reducing the diameter of the heat pipe and increasing the heat transfer coefficient by the tube group. In order to construct an arrangement that fully exhibits the effect of the tube group, it is necessary to have at least two rows, and the number of tubes per row (number of stages) is preferably at least three. That is, the minimum number required in the embodiment of FIG. 1 is 6 per side, making a total of 12.

8. Located within a few meters from the heat receiving plane and 41 o o K
Must have a crushing strength of q/ad. Taking into account the sufficient surface area increase rate of the insertion part and the sufficient surface area increase rate of the heat dissipation part to reduce the thermal resistance of the heat receiving block, and considering the conditions of 41 holes as the basis, the effect of the present invention will be increased by +11. It is desirable that the diameter of the heat pipes be 12 m or less, and that the number of heat pipes be at least 12 or more.

(b) A heat radiator according to the present invention, in which the heat absorbing portion of each heat pipe and the heat receiving metal block are closely bonded to each other with an adhesive having relatively high thermal conductivity and good heat resistance.

(C) The heat absorbing part of each heat pipe and the heat receiving metal block are inserted through an electrical insulating film that has relatively good thermal conductivity and heat resistance, and there is no electrical connection between them. The heat sink according to the present invention is configured to be in an insulated state and thermally connected.

(d) A heat radiator according to the present invention, in which an annular fin heat radiator is used in combination with a part of the heat pipe heat radiator in the heat exchange section.

The heat dissipation section structure of the heat pipe used in the present invention is, in principle, an unfinned metal tube or a loaf-in tube, but is not limited to these, and has the necessary heat dissipation capacity within the limited heat exchange section volume. In order to achieve a good effect, fins may be used in part or all of the parts. However, in order not to lose the turbulent flow generation effect of the heat pipe group, it is necessary to use individual annular fins. Furthermore, it cannot be applied to the row of heat pipes closest to the heat receiving surface. As can be seen from FIG. 1, this is because there is a risk of contact with the heat exchange part of the radiator used adjacently.

(-) The heat pipe type heat radiator according to the present invention is not necessarily implemented with the heat receiving plane held vertically. In each of the embodiments illustrated in FIGS. 1 to 7, the heat-receiving plane is held horizontally, and forced convection heat radiation and natural convection heat radiation can be performed. In this case, the flow direction of the refrigerant fluid can take various directions in the case of forced convection, but in the case of natural convection, it can only flow in a direction perpendicular to the heat receiving plane.

(f) A radiator according to the present invention, in which the heat-receiving metal block and the heat exchange section are electrically insulated, and water is normally used as the heat medium fluid.

If the heating element to be cooled in a heat pipe type radiator is a semiconductor of the type that provides a potential to the heat exchange part, and if water must be used as the refrigerant fluid, pure water without conductivity may be used as the cooling water. need to be used. However, in the case of the heat pipe type radiator according to the present invention, the base heat pipe and the heat receiving metal block are electrically insulated,
Ordinary water can be used as the refrigerant liquid because it is reliable.

The heat-receiving metal block in each of the above-mentioned embodiments is composed of a stack of flat metal blocks, each having the same number of rows as the number of rows constituting the insertion hole group, and divided by a plane parallel to the heat-receiving surface. A radiator according to the present invention, wherein a predetermined row of insertion holes are drilled from one side edge surface of each metal block in parallel with each other and parallel to the heat receiving plane.

(G) Effects of the Invention The heat pipe type heat radiator according to the present invention has synergistic effects such as reduction in the diameter of the heat pipe, cross arrangement in the heat receiving metal block, and rows of heat pipes in which the distance between the heat pipes is reduced in the heat exchange section. The greatest effect of the structure according to the present invention is that the heat pipe type radiator, which was conventionally considered to be at its limit, is able to achieve revolutionary high performance. That is, the heat resistance value of the heat-receiving metal block in the case of 64 heat pipes with a diameter of 10 m, which was given as an example in the section (e) on the effect, is grouped in rows, is 0.0004 ('C/W).
, the overall thermal resistance value of the heat pipe group is 0.0009 ('C
β], the heat resistance value o, ooo2 (℃/W) of the resistance due to the adhesive at the adhesive part of the heat pipe and the block, the value of the heat radiation resistance during forced convection in the heat exchanger 0,00875 ('Cβ
The total l'to, 01[° C./w] is the value of the total thermal resistance that indicates the performance of the heat sink in this case. Compared to the large capacity thyristor heat dissipation resistance level of the conventional structure, which is o, o2c/W), it can be said that this is an epoch-making performance. This value is 121 pieces using heat pipes with a diameter of 8w to 4van.
Depending on the 169-piece configuration, the relative value is 0.007 ('Cβ).

It is also possible to construct a heat sink with even higher performance, such as 0.005 ('Cβ).

In addition, since the structure does not rely on fin groups, there is no pressure drop, and even if a fan of the same capacity is used, a faster flow velocity can be obtained, resulting in higher performance.

Furthermore, it is possible to electrically insulate the heat receiving part and the heat exchange part, which has been difficult to put into practical use in the past, and the range of uses of the heat radiator is expanded. It is also possible to cool the heat exchange section with ordinary water, further improving heat dissipation performance, and also making it possible to significantly reduce the size of the heat exchange section.

Another advantage of the structure of the radiator according to the present invention is that maintenance and cleaning are extremely easy.

Furthermore, although not mentioned in the examples, as an effect of the present invention, an extremely thin heat radiator can be constructed.

That is, when the number of layers of heat pipe rows arranged crosswise in a block is reduced, for example, by arranging 10 rows in two to four layers, the block becomes extremely thin and the heat exchanger section It can also be made thinner and smaller to the same extent, and can be effectively applied to small equipment.

Although the present invention is a heat pipe type heat radiator that was devised mainly for heat dissipation in equipment using semiconductor electronic components, the range of its effects is not necessarily limited to heat radiation in such equipment. It can be applied to all other fields as a heat dissipation means that once absorbs heat in the heat receiving metal block, transfers the heat through the heat pipe, and radiates the heat from the heat exchange section.

[Brief explanation of drawings]

Fig. 1 is a schematic configuration explanatory diagram of the first embodiment of the heat pipe type radiator according to the present invention, @ Figs. 2 to 7 are diagrams showing the second to seventh embodiments of the heat pipe type radiator according to the present invention. Schematic configuration explanatory diagrams, FIGS. 8 to 10 show the heat receiving metal block according to the present invention, and FIG. 8 is a front view seen from the heat receiving plane side.
I! Figure 9 is a side view of Figure 8, Figure 1O is a plan view of Figure @8, Figures 11 and 12 are diagrams showing the arrangement of heat pipe groups in the wind tunnel, Figures 13 and 14 are A schematic front view and a schematic side view of the conventional structure, and FIGS. 15 and 16 are explanatory views showing the arrangement of conventional heat pipe insertion holes. 1... Metal block for heat receiving, 2.2-1.2-2...
・Heat pipe, 3...Fin group, 4...Insertion hole,
5... Power thyristor element, 6... Power terminal, 7
...Wind tunnel side plate. Fig. 13 - Schematic diagram of the reverse a front view of the 1λ coming pattern - Fig. 15 - Tsukuda Ishu of the 14th night side run - Fig. 16 - Ri 11 -

Claims (15)

[Claims] (1) A heat-receiving metal block in which one or both of the opposing planes is a heat-receiving plane and the other plane has an insertion hole for inserting a heat pipe, and the heat-absorbing part of the container is a heat-receiving metal block. A heat pipe type heat radiator consisting of a heat pipe which is tightly inserted into the insertion hole of the block and thermally connected, and a heat exchange part whose main element is the heat radiation part of the heat pipe container. and is configured to meet all of the configuration conditions for each item below. (b) A large number of insertion holes are drilled from multiple sides of the heat receiving metal block toward the inside of the block, and these insertion holes are parallel to each other and all of them are in the heat receiving plane. The hole must be drilled parallel to the (b) When the insertion holes provided in the heat-receiving metal block are viewed from the heat-receiving plane side, each insertion hole in the group of insertion holes drilled from one side is drilled from the other side. When viewed from each side, each insertion hole in the insertion hole group drilled from each side must intersect with each insertion hole in the insertion hole group drilled from the other side. The holes shall be drilled so that they never intersect with any of the insertion holes in the group of insertion holes. (2) The heat pipe type heat radiator according to claim 1, wherein the insertion hole and the heat pipe have respective inner diameters and outer diameters compared to the volume of the heat receiving metal block and the area of the heat receiving plane. The heat absorbing part and insertion hole of each heat pipe are made of an adhesive material with relatively high thermal conductivity and good heat resistance. A heat pipe type radiator characterized by being closely bonded to each other. (3) The heat pipe type heat radiator according to claim 1, wherein the insertion hole and the heat pipe each have an inner diameter and an outer diameter compared to the volume of the heat-receiving metal block and the area of the heat-receiving plane. The heat absorbing portion and insertion hole of each heat pipe are made of electrically insulating material with relatively good heat conductivity and heat resistance. 1. A heat pipe type heat radiator, characterized in that the heat pipe type heat radiator is inserted through a body membrane, and the two are electrically insulated and thermally connected. (4) In the heat pipe type heat radiator according to claim 1, the heat radiating portion of the heat pipe inserted in close proximity to the heat receiving plane of the heat receiving metal block is made of a finless metal tube or a finless metal tube. A heat pipe type heat radiator characterized in that a finned tube is used, and for a given heat pipe among other heat pipes, a metal tube in which annular fins are individually formed is used for the heat radiation part. . (5) In the heat pipe type heat radiator according to claim 1, the heat receiving metal block is held such that the heat receiving plane is perpendicular, and the heat radiating portion of the heat pipe group is oriented toward the heat receiving plane. It is aligned and extended in either the right side direction, left side direction, or both left and right directions, and the heat exchange part of the radiator is formed on either one side or both sides of the heat receiving metal block. A heat pipe type radiator characterized by: (6) In the heat pipe type heat radiator according to claim 1, the heat receiving metal block is held such that the heat receiving plane is vertical, and the heat radiating portion of all the heat pipes is the heat receiving metal block. It is aligned and extended in the direction of the upper surface,
A heat pipe type radiator characterized in that a heat exchange part of the radiator is formed on the upper side of a heat receiving metal block. (7) The heat pipe type heat radiator according to claim 1, wherein the heat receiving metal block is held such that the heat receiving plane is horizontal, and the heat radiating portion of the heat pipe group is the heat receiving metal block. A heat pipe type radiator characterized in that the heat pipe type radiator is arranged and extended in the direction of one or more predetermined side surfaces to form a heat exchange part of the radiator on the side surfaces. (8) In the heat pipe type heat radiator according to claim 1, the heat-receiving metal block is basically formed in a prismatic three-dimensional shape whose bottom surface is a heat-receiving plane that is a predetermined polygonal plane. Features a heat pipe type radiator. (9) The heat pipe type heat radiator according to claim 1, wherein the heat absorbing portion of each heat pipe of the heat pipe group is closely inserted into each insertion hole of the heat receiving metal block. The heat transfer section of each heat pipe may be bent or straight, so that the heat dissipation section of each heat pipe is placed at a predetermined position in the heat exchange section of the radiator. 1. A heat pipe type radiator, characterized in that the heat pipe type radiator is introduced and arranged in a tube group arrangement in a predetermined stage row to constitute a heat exchange part of the radiator. (10) In the heat pipe type radiator according to claim 1, the container forming the heat radiating part of each heat pipe in the heat exchange part of the radiator may be a finless metal tube or a roller. In principle, finned tubes are used, but even if fins are required due to the required heat transfer area, metal tubes in which each tube is individually provided with a group of small-area annular fins with a fin height of 6 mm or less. A heat pipe type radiator characterized by using. (11) The heat pipe type heat radiator according to claim 1, wherein each heat pipe in the heat pipe group is formed of a thin-walled thin-tube container made of copper or aluminum with an outer diameter of 12 mm or less, and is used for receiving heat. A group of insertion holes with an inner diameter of 12.2 mm or less are drilled in the metal block, and the insertion holes opened on one side are arranged in a row in a direction parallel to the heat receiving surface, and in a direction perpendicular to the heat receiving plane. When a row of holes is referred to as a stage, holes are drilled in a predetermined number of stages and rows, and each row has at least three (three stages) or more insertion holes arranged at equal intervals to form a heat receiving plane. At least two rows are arranged between the bottom surfaces of the heat-receiving metal block, and the gaps between these rows are filled with insertion holes drilled from the side surface. There are rows of insertion holes that are aligned and drilled from the other side, intersecting the rows of the groups, and the heat receiving metal block as a whole has at least 12 insertion holes. 1. A heat pipe type heat radiator, characterized in that the heat radiator as a whole is constructed using at least 12 or more heat pipes inserted and connected as described above. (12) The heat pipe type heat radiator according to claim 3, wherein the heat absorbing portion of each heat pipe and the insertion hole of the heat receiving metal block are electrically insulated from each other and are inserted and connected. A heat pipe type radiator characterized in that natural convection or forced convection cooling water is used as a heat dissipation medium in a heat exchange section. (13) In the heat pipe type heat radiator according to claim 11, in the heat receiving metal block, the center distance of the heat pipes in each row and between each row of the heat pipe insertion and connection arrangement is determined by the insertion hole. The distance between the center of the heat pipe in the row closest to the heat receiving plane and the heat receiving plane is 1/2 of the distance between the centers of the heat pipes in each row. A heat pipe type radiator characterized by being arranged as close together as possible technically. (14) The heat pipe type radiator according to claim 11, wherein a group of heat pipes aligned and extended from a plurality of side surfaces of a heat receiving metal block are integrated again in a heat exchange section, and A group of heat pipes aligned and extended from the other side is introduced into the heat exchange section, which is constituted by a group of heat pipes aligned and extended from one side of the side, and the whole has a high-density row of stages. A heat pipe type radiator characterized in that the heat pipe type radiator is configured as a relatively small-volume heat exchange section arranged in an array. (15) The heat pipe type heat radiator according to claim 11, wherein the heat receiving metal block is divided into the same number of blocks as the number of rows constituting the insertion hole group and on a plane parallel to the heat receiving plane. A predetermined row of insertion holes are cut from one side edge surface of each flat metal block in parallel with each other and parallel to the heat receiving plane. A heat pipe type radiator characterized by having holes.