JP2009243864A - Inner surface grooved pipe for heat pipe, and heat pipe - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inner surface grooved pipe, excellent in workability and productivity, stable in quality, and excellent in cooling performance. <P>SOLUTION: In the inner surface grooved pipe for a heat pipe made of copper or copper alloy provided with fins 3 extending to a direction in parallel with or inclined to a pipe axial direction on an inner surface of a pipe 1, a lead angle of the fin 3 to the pipe axis is from 0 to 5 degrees. Regarding a shape of the fin 3 on the pipe axis orthogonal cross section, 40 quantity% of fins or more have fin apexes divided to be a V shape or a Y shape. In the pipe axis orthogonal cross section, two or more of five fins continuously aligned have notch-shaped concave parts 4, each of which is provided in a direction in parallel with the pipe axis, or in a direction of climbing a slope, or in a direction of going down the slope, on one or both sides of the slope formed from the apex of the fin 3 to a bottom part of a groove 2 between the fins 3. A crest angle θ of the apex of the fin 3 which does not have a V-shaped or Y-shaped apex form is 40 degrees or smaller. A groove bottom width L between the fins 3 formed within the pipe axis orthogonal cross section is 0.1-0.3 mm. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a heat pipe used for heat dissipation and cooling of a central processing unit (CPU) of a personal computer and the like, and an inner grooved pipe used for manufacturing the heat pipe and using water as a refrigerant (working fluid).

  Recently, as the speed of personal computers increases, the amount of heat generated by the CPU increases, and high heat transfer performance is required for heat pipes used for cooling the CPU. In addition, notebook computers are being made thinner due to portability requirements. Due to the necessity of being built into a thin laptop computer with a large amount of heat generated in this way, the heat pipe is provided with grooves on the inner surface of the heat transfer tube made of copper or copper alloy, and fins are formed as protrusions between the grooves. Thus, an internally grooved tube having improved heat transfer performance by increasing the contact area between the heat transfer tube and water as the refrigerant (working fluid) is used. This internally grooved tube is flattened and used as a heat pipe. FIG. 2A is a cross-sectional view of an internally grooved tube that has been flattened, and FIG. 2B is a cross-sectional view that shows a curved portion of the internally grooved tube that has been flattened. As shown in FIG. 2, the internally grooved tube 1 is flattened to have a shape in which a semicircular curved portion 11b is connected by a straight portion 11a in a cross section perpendicular to the tube axis. And the curvature radius in the pipe inner surface of the curved part 11b is smaller than the inner radius of the original inner surface grooved pipe. Therefore, the fins in the curved portion of the pipe approach each other, the width of the groove between the fins in the curved portion is narrowed, and the groove portion of the curved portion, particularly the groove cross-sectional area near the center of the curved portion is reduced. Therefore, the amount of hydraulic fluid that can be held in the groove is reduced and the flow of hydraulic fluid is inhibited.

  The working fluid in the heat pipe exists in the state of gas and liquid. The hydraulic fluid removes heat from the tube wall in the vicinity of a heat source (evaporator side) such as a CPU, and changes from a liquid to a gas. For this reason, the pressure on the evaporation section side becomes high, and the working fluid that has become a gas flows through the central portion of the pipe cross section to the heat radiation section side (condensing section side) where the pressure is low. The gas that has flowed to the heat radiating portion releases heat to the tube wall, turns the gas into a liquid, and flows through the groove portion between the fins from the condensation portion side to the evaporation portion side by capillary force.

  Conventionally, heat pipes have an internally grooved tube that has a grooved lead angle with respect to the tube axis and an inclined portion at the base of the fin, making it easy for hydraulic fluid to flow from the condensing part to the evaporation part. Has been.

  For example, Patent Document 1 discloses that a plurality of grooves having a lead angle with respect to a tube axis are formed on the inner surface of a tube material by rolling, and a smooth gentle slope provided on the boundary between the fin inclined portion and the groove bottom portion is provided. By optimizing the thickness, an internally grooved tube with improved workability and tool life has been proposed.

  Further, in Patent Document 2, a plurality of U-shaped main grooves having a parallel or lead angle to the tube axis and a plurality of V-shaped sub-grooves having crossing angles with respect to the main grooves are formed by rolling. A method is disclosed in which a plate material is intermittently formed, and thereafter a groove forming surface is rounded in an arc shape by roll forming, and a tubular body is formed by electric sewing. And this inner surface grooved tube forms a tubular groove by partially narrowing the opening width of the groove upper part with respect to the formed V-shaped fin, and it is made easy to generate bubbles in this tubular groove. ing. This bubble serves as a nucleus to promote evaporation, thereby increasing the vaporization efficiency and further improving the transport efficiency of the hydraulic fluid due to the surface tension in the groove.

  In Patent Document 3, a plurality of main grooves extending in parallel or spirally with the tube axis are formed on a plate by rolling, and then V-shaped sub grooves that intersect the main grooves at a constant angle are intermittently formed. A method is disclosed in which a sheet material is formed, then the groove forming surface is rounded in an arc shape by roll forming, and the tube body is formed by electric sewing. At the intersection of the main groove and the V-shaped groove formed on the inner surface of the tube, the ridge formed between the main grooves is divided by the V-shaped groove to form an inclined wall inclined right and left. Between the adjacent inclined walls, tubular grooves having an opening width smaller than the bottom are intermittently formed. Regions where only the ridges are formed and regions where the tubular grooves are formed are alternately formed, so that bubbles of hydraulic fluid are easily generated in the tubular grooves, and regions where only the ridges are formed. In this case, the bubbles are not retained, so that the reduction in heat transfer efficiency between the heat transfer fluid and the heat transfer tube is reduced even when the flow rate of the hydraulic fluid is large.

JP 2003-222480 A JP-A-3-234302 JP-A-6-101986

  However, the above-described prior art has the following problems. In the heat pipe, the condensate flowing through the condensing part has a velocity component perpendicular to the fins. The velocity component perpendicular to the fins of the condensate increases with an increase in the lead angle of the inner groove with respect to the tube axis, and the fins act strongly as resistance elements, and the flow of condensate flowing through the groove bottom The length becomes longer as the lead angle increases, and the flow rate of the condensate passing through a certain section of the heat pipe becomes smaller. In addition, the flow direction of the steam flowing from the evaporation section to the condensation section in the center of the tube and the working fluid flowing from the condensation section to the evaporation section along the tube wall is opposite, and friction occurs at the boundary. If the flow rate of the condensate drops or the friction between the vapor and the condensate prevents the flow of the condensate from the condensing part side to the evaporating part side, the working liquid is insufficient on the evaporating part side and dry. The heat transfer coefficient drops rapidly, so that it can no longer serve as a heat pipe. Since the inner grooved tube described in Patent Document 1 has a large lead angle, in addition to the low flow rate of the working fluid, the contact area between the steam flowing in the center of the tube cross section and the condensate flowing along the tube wall is wide. Since friction is likely to occur at the boundary, the working fluid is insufficient on the evaporation side, and it is easy to dry out, so that sufficient cooling performance cannot be obtained. Further, since the lead angle is large, the grooved plug is greatly worn when the groove is formed on the inner surface of the tube, the workability is poor, and the processing cost is increased.

  Furthermore, the internally grooved tube described in Patent Document 1 is provided with a smooth gentle slope at the boundary between the fin inclined portion and the groove bottom, and the workability of the internally grooved tube is improved by defining the height of the gentle slope. However, since the width at the bottom of the groove of the gentle slope is wide, the area of the groove is reduced, and the amount of hydraulic fluid flowing through the groove is reduced, leading to a decrease in cooling performance.

  In addition, since the internally grooved tubes described in Patent Documents 2 and 3 are formed into a tube by electro-sewing after performing groove processing and roll forming by rolling on the plate material, the welded portion by electro-sewing processing is formed on the tube inner surface. This has the disadvantage of being unstable and not stable in quality.

  The present invention has been made in view of such problems, and provides an internally grooved tube for heat pipe and a heat pipe that are excellent in workability and productivity, stable in quality, and excellent in cooling performance. For the purpose.

  An inner grooved tube for a heat pipe according to the present invention is an inner grooved tube for a heat pipe made of copper or copper alloy in which a fin extending in a direction parallel to or inclined with respect to the tube axis direction is formed on the inner surface of the tube. The lead angle β with respect to the tube axis is 0 to 5 °, and the shape of the fin in the cross section perpendicular to the tube axis is such that 40% by mass or more of fins are divided into V-shaped or Y-shaped fins, In the cross-section perpendicular to the tube axis, the direction parallel to or up the tube axis on one or both sides of the slope formed from the top of the fin to the groove bottom at a ratio of 2 or more of the 5 fins arranged in a row Alternatively, a notch-shaped recess is formed in the direction of going down the slope, and the peak angle θ of the top of the fin that does not have the V-shaped or Y-shaped top shape is 40 ° or less and is formed in the cross section perpendicular to the tube axis. Between the fins Groove bottom width L is being 0.1 to 0.3 mm.

  Furthermore, the internally grooved pipe for heat pipes according to the present invention is formed as a projection between the first grooves by forming a first groove by rolling the inner surface of the pipe with a first grooved plug. The fin is formed on the inner surface of the pipe, and after forming the first groove, by rolling the inner surface of the pipe with a second grooved plug to form the second groove on the top of the fin, It is preferable that at least some of the tops of the fins are divided.

  The heat pipe according to the present invention is characterized in that the above-mentioned inner grooved pipe for heat pipe is formed by flattening the circular cross section thereof.

  According to the internally grooved pipe for a heat pipe of the present invention, performance is improved by providing a notch-like recess on the fin slope. That is, in the evaporation part, the notch-shaped dent becomes the starting point of bubbles, and nucleate boiling is likely to occur, and the maximum heat capacity increases. Further, in the condensing part and in the intermediate region between condensing and evaporation, the notch-like dent facilitates the flow of the working fluid to the evaporating part side by the capillary force, and the thermal resistance is lowered. Further, in the inner grooved tube of the present invention, since the second groove is formed at the top of at least a part of the fin and the fin top is divided, the fin whose top is divided into a V shape or a Y shape is the upper portion of the groove. Since the groove shape is close to a tube, a high capillary force is obtained, and the boundary area between the phase of the hydraulic fluid flowing through the groove and the gas phase flowing through the center of the tube is reduced, so that the gas Friction does not occur between the liquid phases, and the hydraulic fluid is continuously supplied to the evaporation section side, so that the cooling efficiency is high and it is difficult to dry out.

  In addition, the heat pipe in which the circular cross section of the inner surface grooved tube for heat pipe of the present invention is formed into a flat shape is formed by rolling the groove shape with a grooved plug on the inner surface of the tube. There is no welded part by electro-sewing process, it is stable in quality, and since the lead angle of the formed groove with respect to the tube axis is small, wear of the grooved plug can be suppressed, and the workability and productivity are excellent.

  Hereinafter, embodiments of the present invention will be specifically described with reference to the accompanying drawings. 1A is a cross-sectional view showing a part of an internally grooved tube in a tube axis orthogonal cross section in an internally grooved tube according to an embodiment of the present invention, and FIG. 1B is a perspective view of FIG. FIG. 3, FIG. 3 is a partially enlarged cross-sectional view of FIG. 1 (a), FIG. 4 is a cross-sectional view in a tube axis parallel cross section, and FIGS. 7 and 8 are views after flattening the internally grooved tube for heat pipe of this embodiment It is the schematic which shows the cross section cut | disconnected by the curved part in the pipe-axis direction.

  First, the shape of the inner grooved tube of the present invention will be described. As shown in FIG. 1A and FIG. 4, the internally grooved tube has a plurality of grooves 2 spirally formed on the inner surface of the tube 1 in a direction parallel to or inclined with respect to the tube axis direction. Fins 3 that extend in a spiral shape are formed as protrusions therebetween. The fin 3 has a trapezoidal shape in which the top width is smaller than the bottom, a round trapezoidal shape with a top that is smaller than the bottom and an arc at the top, an inverted trapezoid with a top width greater than the bottom, V It has the shape of a letter or Y. As shown in FIGS. 1 and 3, in the present invention, the fins 3 are formed from the top of the fin 3 to the groove 2 at a ratio of two or more of the five fins continuously arranged in the cross section perpendicular to the tube axis. A notch-like recess 4 is formed on one side or both sides of the fin slope formed over the bottom in a direction parallel to the tube axis, or in a direction up or down the slope. Further, a part of the fin 3 is further divided to form a V shape or a Y shape in the cross section perpendicular to the tube axis. In the present invention, the lead angle β of the groove 2 with respect to the tube axis direction is 0 to 5 °. Furthermore, the notch-shaped dent 4 may exist in the entire height direction from the top of the fin on the inclined surface of the fin 3 to the boundary with the groove, or may be interrupted in the middle. Moreover, it is preferable that the notch-shaped dents 4 are arranged at regular intervals in the fin longitudinal direction. Further, in a fin not having a V-shaped or Y-shaped shape, the peak angle θ of the fin 3 not having the V-shaped or Y-shaped top shape is 40 ° or less, and the groove of the groove 2 formed between the fins and the fins. The bottom width L is 0.1 to 0.3 mm, preferably the peak angle θ is 0 to 30 °, and the groove bottom width L is 0.13 to 0.2 mm. Furthermore, fins having a V-shaped or Y-shaped shape at the top are included in an amount of 40% or more of the whole, preferably 50% or more of the whole.

  Next, a method for manufacturing an internally grooved tube according to an embodiment of the present invention will be described. First, a grooved plug having a spiral groove formed on the surface and a reduced diameter plug are inserted into the raw tube, and a die that contacts the outer surface of the raw tube is provided at the position of the plug. Then, by pulling out the raw pipe, the raw pipe is reduced in diameter by a diameter reducing die, and the reduced diameter plug is held in position against the pulling force of the raw pipe through the raw pipe, and the groove The attached plug is held in that position in a floating state via the connecting shaft. The grooved plug is rotatably connected to the reduced-diameter plug, and at the position of the grooved plug, a plurality of rolling balls or a plurality of rolling rolls are arranged on the outer surface of the pipe so as to perform planetary rotation. When the raw tube is pressed toward the grooved plug by the ball making or the rolling roll, the inner wall of the raw tube enters the groove of the grooved plug and corresponds to the groove of the grooved plug on the inner surface of the raw tube. Fins 3 are formed. Further, the fin portion of the grooved plug becomes the groove 2 on the inner surface of the raw tube, and the groove shape on the outer surface of the grooved plug is transferred to the inner surface of the raw tube to become the fin 3. The shape of the fin 3 formed at this time is a trapezoidal shape whose top width is smaller than the bottom portion or a round trapezoidal shape whose top portion is smaller than the bottom portion and whose top portion has an arc shape. At this time, if the radius of curvature at the boundary between the top of the grooved plug and the groove slope is sufficiently small with respect to the fin height, the inside of the grooved plug groove of the tubular wall at the boundary between the top of the grooved plug and the slope of the groove Part of the fin 3 that is formed in the form of a cutout is formed on one or both sides of the fin slope formed from the top of the fin 3 to the bottom of the groove 2 between the fins 3. An unfilled recess 4 is formed. In addition, when the tube wall on the inner surface of the fin tube that has entered the groove of the grooved plug and has become a fin shape passes between the rolling roll or rolling ball and the grooved plug, the grooved plug reverses the drawing. A notch-like recess 4 is formed on the fin slope generated on the inner surface of the pipe by receiving the direction drag. Next, when the rolling process using the second grooved plug is performed on the inner surface of the pipe on which the first groove is formed by the rolling process using the first grooved plug, the second groove becomes the fin 3. The top of at least a part of the fins 3 is divided. A part of the fin 3 formed by applying the first groove and having a trapezoidal shape and a round trapezoidal shape at the top in the cross section perpendicular to the tube axis is divided by the second groove, and the trapezoidal shape and the top In addition to the round trapezoidal die, inverted trapezoidal and V-shaped and Y-shaped fins having a fin top width larger than the bottom are formed.

  Hereinafter, the reason for limiting each numerical value will be described.

“Lead angle β: 0 to 5 °”
When the inner grooved tube is flattened as described above, the inner grooved tube 1 has a shape having a straight portion 11a and a curved portion 11b as shown in FIG. When this flattened inner surface grooved tube 1 is used as a heat pipe, the fins in the curved portion 11b of the tube approach each other, and the width of the groove between the fins is narrowed. The amount of hydraulic fluid circulating to the side decreases. The broken lines in FIGS. 7 and 8 indicate fins that are affected by the curved portion due to flattening, and the solid lines indicate fins that are not affected by the curved portion due to flattening. 7 shows a case where the lead angle β is small, and FIG. 8 shows a case where the lead angle β is large. As shown in FIG. 8, as the lead angle increases, the number of fins passing through the curved portion in the pipe per unit length increases, and therefore the performance decreases. Furthermore, while the vapor flowing from the evaporating part to the condensing part is a flow almost parallel to the tube axis, the flow of the hydraulic fluid flowing from the condensing part to the evaporating part is a velocity component perpendicular to the fin slope due to the lead angle. As the lead angle increases, the flow is more strongly inhibited. Further, the hydraulic fluid that has become liquid in the condensing part flows through the bottom of the groove toward the evaporation part due to the capillary force. However, when the lead angle β increases, the flow length of the hydraulic fluid increases accordingly and the flow becomes slower. And if the working fluid is insufficient on the evaporation part side due to a decrease in the circulating amount of the working fluid, it becomes easy to dry out, and the cooling performance is drastically lowered. Furthermore, when the lead angle is large, when the groove is machined in the pipe inner surface, the grooved plug is greatly worn, the workability is lowered, and the machining cost is increased. When the lead angle exceeds 5 °, in the flattened pipe, the frequency of the groove area decreasing in the curved part of the pipe increases and the circulation amount of the hydraulic fluid decreases, and the speed orthogonal to the fin slope of the hydraulic fluid Ingredients increase, and the flow length of the working fluid increases, making it easier to dry out. Accordingly, the lead angle β between the groove and the tube axis direction is 0 to 5 °.

“Percentage of protrusions with cutout dents: 2 or more of the 5 in a row”
When a notch-like recess is provided on the slope of the protrusion, the notch-like recess becomes a starting point of bubbles in the evaporation part, and nucleate boiling is likely to occur, and the maximum heat capacity increases. Further, in the condensing part and in the intermediate region between condensing and evaporation, the notch-like dent facilitates the flow of the working fluid to the evaporating part side by the capillary force, and the thermal resistance is lowered. If the ratio of protrusions with notch-shaped dents is less than two of the five continuous, the maximum heat capacity cannot be sufficiently increased and the thermal resistance is not sufficiently reduced, and the ratio of protrusions with notch-shaped dents is continuous. If two or more of these five are used, the frequency of nucleate boiling will increase, and it will be easier to supply the working fluid from the condensing unit to the evaporating unit side by capillary force, so the cooling efficiency will increase and it will be difficult to dry out. Therefore, the ratio of the protrusions having a notch-like recess is two or more of the five consecutive.

“Crest angle θ: 0 to 40 °, groove bottom width L: 0.1 to 0.3 mm”
In the case of the same number of protrusions and the same groove bottom width, the smaller the peak angle, the closer the angle between the protrusion and the groove bottom becomes, the closer the groove shape is to a tube, and the higher the meniscus formed by the hydraulic fluid. High capillary force can be obtained. Therefore, the flow of hydraulic fluid from the condensing part side to the evaporation part side is improved, and the cooling performance is improved. Also, as the groove bottom width increases, the groove area increases and the amount of hydraulic fluid that can be retained increases, so the amount of hydraulic fluid circulated increases and cooling performance improves. As the height is lowered, the capillary force cannot be obtained, and the cooling performance is lowered. When the summit angle exceeds 40 °, the capillary force decreases and the circulating amount of the hydraulic fluid decreases, and the contact area between the groove or the slope of the projection and the gas phase increases, and the friction at the boundary between the gas phase and the liquid phase increases. As a result, the flow of the hydraulic fluid is likely to be hindered, so that the cooling performance is deteriorated. When the groove bottom width L is less than 0.1 mm, the hydraulic fluid hardly enters the groove due to the surface tension of the hydraulic fluid, and when the groove bottom width L exceeds 0.3 mm, the meniscus height decreases and the capillary force is reduced. The cooling performance decreases due to the decrease. Therefore, the peak angle θ of the protrusion is 0 to 40 °, and the groove bottom width L is 0.1 to 0.3 mm.

“V-shaped or Y-shaped fins on top: 40% or more of the total”
The V-shaped or Y-shaped fin shape narrows the opening width at the top of the groove, and the groove shape is close to a tube, so that a high capillary force can be obtained, and the phase of the working fluid flowing in the groove and the gas phase flowing in the center of the tube Since the boundary area is reduced, friction does not occur at the boundary, and the hydraulic fluid continues to be supplied to the evaporation section, so that the cooling performance is improved. If the number of fins having a V-shaped or Y-shaped shape on the top of the projection is less than 40% by volume, the V-shaped or Y-shaped is better than the improvement in capillary force and the amount of hydraulic fluid supplied from the condensing unit to the evaporation unit. The decrease in the capillary force due to the fins having no fin shape and the decrease in the amount of hydraulic fluid supplied due to the increase in friction at the boundary between the liquid phase and the gas phase are larger, and the cooling performance decreases. Accordingly, the number of fins having a V-shaped or Y-shaped shape at the top of the protrusion is 40% or more of the whole.

  The effects of the embodiments of the present invention will be described below in comparison with comparative examples. Tables 1 to 3 below show the shape conditions of the comparative examples and examples.

  In the production of the heat pipe of this example or comparative example, a groove (fin) was formed by the above-described manufacturing method on a base tube having an outer diameter of 10 mm and a wall thickness of 0.40 mm, and the outer diameter was 6 mm and the bottom wall thickness was 0. An internally grooved tube machined to 3 mm was used. Tables 1 to 4 below show the configurations (shapes and dimensions) of this internally grooved tube.

  And after cut | disconnecting this inner surface grooved pipe | tube to length 210mm, the inner surface was wash | cleaned and the oil component was removed. Next, one end of the tube was reduced in diameter by a section of 5 mm in the aperture length and closed by TIG welding, and then the diameter of the other end was reduced in a section by a length of 5 mm. Next, after inserting 0.6 ± 0.01 cc from the end of the tube not TIG-welded, the tube is warmed so that water does not leak, and the open end is closed by TIG welding while evaporating the water in the tube. Then, the pipe having both ends reduced in diameter by 5 mm sections and further closed at both ends by TIG welding to a length of 200 mm is bent at a position of 100 mm from the pipe end after flattening as shown in FIG. It was bent into an L shape with a radius of 30 mm. The dimensions of this tube are as shown in Table 4.

  FIG. 6 shows an experimental apparatus used for measuring the performance of the internally grooved tube of this embodiment. In the heat pipe 11, a section 25 mm from the end of the pipe was heated by a heater 12 as a heating unit. In this example, after heating the heat pipe 11 for 10 minutes with an input power of 30 W by the heater 12, the heating part temperature, the condensing part temperature and the ambient temperature were measured using a T-type thermocouple thermometer. Here, the heating part temperature is the surface temperature of the heat pipe 11 at the position 14 mm from the pipe end heated by the heater 12, and the condensing part temperature is the heat pipe at the position 15 mm 20 mm from the pipe end not heated by the heater 12 of the heat pipe 11. It is the surface temperature, and the atmospheric temperature is the temperature at the atmospheric temperature measurement point 16 during the experiment.

  The performance of the heat pipe is evaluated using the parameters calculated by the following formulas 1 and 2.

Here, Q is the cooling efficiency used as a parameter indicating the cooling performance of the pipe, and is a value indicating the degree of increase in the temperature of the heating section with respect to the heating by the heater 12. Here, _Th is the heating part temperature, the surface temperature of the heat pipe 11 at the position 14 mm from the end of the tube to be heated, _Ta is the ambient temperature, and W is the input power by the heater. Since the one where there is little raise of heating part temperature is excellent in the cooling performance of a heat pipe, it can be judged that the one where Q value is small is excellent in cooling performance.

Here, ΔT is a temperature difference between the heating part and the condensing part of the pipe, and is a value used to determine the presence or absence of dryout that occurs in the pipe flow in which steam and liquid mix and flow like a heat pipe, The smaller the value, the better the performance. That is, when the ratio of the vapor increases and the liquid cannot flow through the tube wall, the heat transfer rate rapidly decreases, so that the heat pipe cannot play its role. _Tc is the temperature of the condensing part, which is the surface temperature of the heat pipe at a position 15 mm from the end of the pipe not heated by the heater 12 of the heat pipe 11.

  As shown in Tables 1 to 3, since Examples 1 to 13 have the lead angle β that satisfies Claim 1, the cooling performance is superior to that of Comparative Example 4 that does not satisfy Claim 1. Further, in Examples 1 to 13, the ratio of the protrusions having a notch-like recess satisfies Claim 1, so that the cooling performance is superior to Comparative Examples 1 and 2 that do not satisfy Claim 1. Further, in Examples 1 to 13, the peak angle θ of the protrusions satisfies the first aspect, so that the cooling performance is excellent as compared with Comparative Example 3 that does not satisfy the first aspect. Further, in Examples 1 to 13, the proportion of fins having a V-shaped or Y-shaped shape at the top satisfies Claim 1, so that the cooling performance is superior to Comparative Example 5 that does not satisfy Claim 1. .

(A) is sectional drawing which shows a part of pipe axis orthogonal cross section in the inner surface grooved pipe | tube of this embodiment, (b) is the perspective view. (A) is sectional drawing of the internally grooved pipe which was flattened, (b) is sectional drawing which shows the curve part of the internally grooved pipe which was flattened. It is a figure which shows a fin top part and a groove part. It is sectional drawing of the pipe axis orthogonal cross section in the inner surface grooved pipe | tube of this embodiment. It is a figure which shows the heat pipe used for the test. It is a figure which shows the testing apparatus of cooling heat transfer performance. It is the schematic which shows the cross section which cut | disconnected the curved inner surface pipe | tube for heat pipes of this embodiment in the pipe-axis direction after flattening. It is the schematic which shows the cross section which cut | disconnected the curved inner surface pipe | tube for heat pipes of this embodiment in the pipe-axis direction after flattening.

Explanation of symbols

1: inner grooved tube, 2: groove, 3: fin, 4: notch-shaped dent, 11: heat pipe, 11a: straight part, 11b: curved part, 12: heater, 14: heating part temperature measurement point, 15: condensation part temperature measurement point, 16: atmosphere temperature measurement point, θ: peak angle, β: lead angle, L: groove bottom width, W: input power by heater, _Th : heating part temperature, _Ta : atmosphere temperature , T _c : condensing part temperature

Claims (3)

In an internally grooved tube for a heat pipe made of copper or copper alloy, in which a fin extending in a direction parallel to or inclined with respect to the tube axis direction is formed on the tube inner surface, the lead angle β of the fin to the tube axis is 0 to 5 ° The shape of the fin in the cross section perpendicular to the tube axis is 40 fin% or more of fins with the top of the fin divided into a V-shape or a Y-shape. Notch-shaped recesses are formed in one or both sides of the slope formed from the top of the fin to the groove bottom at a ratio of two or more of the fins in a direction parallel to the pipe axis or in a direction up or down the slope. The peak angle θ of the top of the fin not having the V-shaped or Y-shaped top shape is 40 ° or less, and the groove bottom width L between the fins formed in the cross section perpendicular to the tube axis is 0.1 to This is 0.3mm An inner grooved tube heat pipe according to claim. By forming the first groove by rolling the inner surface of the tube with a first grooved plug, the fin is formed on the inner surface of the tube as a protrusion between the first grooves. After forming the groove, at least a part of the top of the fin is divided by rolling the inner surface of the pipe with a second grooved plug to form the second groove on the top of the fin. The internally grooved pipe for a heat pipe according to claim 1. 3. A heat pipe, wherein the internally grooved tube according to claim 1 or 2 has a circular cross section formed into a flat shape.

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