JP2011222692A - Cooling device and electronic device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling device capable of saving power consumption required for cooling while efficiently cooling a heat generating part of an electronic device.SOLUTION: One embodiment of the cooling device comprises an air cooling fan, a cooling liquid channel, and a driving unit. The air cooling fan cools a heat generation part of the electronic device. Through the cooling liquid channel, cooling liquid for cooling the heat generation part flows. The driving unit transports the cooling liquid flowing through the cooling liquid channel by use of motive power of the air cooling fan.

Description

  The present invention relates to a cooling device and an electronic device for cooling a heat-generating component of the electronic device.

  Conventionally, various cooling devices for cooling a heat-generating component using the rotational force of a motor have been proposed. In addition, a cooling device for electronic devices is also known that uses both air cooling with a fan and liquid cooling with a cooling liquid in order to more efficiently cool the heat generating components of the electronic device.

JP 2004-183610 A

  In a cooling device for electronic equipment that uses both air cooling and liquid cooling, a pump for sending the cooling liquid is required. And when a fan and a pump are each driven with electric power with said cooling device, since the power consumption required for cooling an electronic device increases, there exists a problem that the load to an environment becomes large.

  In view of the above circumstances, there is provided a means capable of further suppressing power consumption required for cooling while efficiently cooling a heat-generating component of an electronic device.

  One aspect of the cooling device includes an air cooling fan, a coolant flow path, and a drive unit. The air cooling fan cools a heat generating component of the electronic device. A coolant that cools the heat-generating component flows through the coolant channel. The driving unit transports the coolant in the coolant channel using the power of the air cooling fan.

  One aspect of the electronic device includes a heat generating component, an air cooling fan, a coolant flow path, and a drive unit. The air cooling fan cools the heat generating component. A coolant that cools the heat-generating component flows through the coolant channel. The driving unit transports the coolant in the coolant channel using the power of the air cooling fan.

  In one aspect of the cooling device, since the cooling liquid in the cooling liquid flow path is transported using the power of the air cooling fan, power consumption used for cooling the electronic device can be suppressed.

2 shows an example of a blade server according to an embodiment. 2 shows a configuration example of a blade according to an embodiment. An example of the first drive unit is shown enlarged. The example of arrangement | positioning of the screw in a cooling fluid flow path is shown. The part of the magnet coupling of the 1st drive part is expanded and shown. An example of the second drive unit is shown enlarged. (A), (b): The example of the cam state change by rotation of a shaft with a cam is shown. The structural example (elongation state) of the pump chamber of a cooling fluid flow path is shown. The structural example (contraction state) of the pump chamber of a coolant flow path is shown. The other structural example of the braid | blade in one Embodiment is shown.

<Description of Embodiment>
Hereinafter, a configuration example of a blade server will be described as an embodiment of a cooling device for an electronic device with reference to the drawings.

  FIG. 1 shows an example of a blade server 100 according to an embodiment. The blade server 100 includes a chassis 101, a blade (computer unit) 102, a power supply unit 103, and a connector board 104. The power supply unit 103 and the connector board 104 are disposed in the chassis 101.

  The chassis 101 accommodates a plurality of blades 102 in a detachable manner. Each blade 102 is connected to a connector board 104 in the chassis 101. The blade server 100 can be replaced or added for each blade 102 when a failure occurs in the blade 102 or when the performance of the server is improved.

  The power supply unit 103 and the connector board 104 are provided in the lower part of the chassis 101. The power supply unit 103 supplies power to each device in the blade 102 via the connector board 104.

  Here, the chassis 101 in one embodiment has a width of about 480 mm, a height of about 300 mm, and a depth of about 550 mm, for example. Further, the blade 102 in one embodiment is a vertical type, and has, for example, a width of about 45 mm, a height of about 280 mm, and a depth of about 450 mm.

  Next, the blade 102 as an electronic device will be described in detail. FIG. 2 shows a configuration example of the blade 102 in one embodiment. In the following description, the vertical direction in the figure is expressed as “vertical”, and the horizontal direction in the figure is expressed as “horizontal”.

  The blade 102 includes a hard disk device 11 for storing information, a substrate 12 on which an electronic circuit as a heat generating component is mounted, an air cooling fan 13 and liquid cooling units (21 to 26) as a cooling device, and a case in which each device is incorporated. 14. The casing 14 has openings 14a and 14b for ventilation on the front side (left side in FIG. 2) and the back side (right side in FIG. 2). Note that the hard disk device 11 shown in FIG. 2 has a size of about 70 mm in length and about 110 mm in width, for example.

  The board 12 includes, for example, an I / O controller hub 15, a memory controller hub 16, a memory 17 that temporarily stores information, and a CPU 18 that plays a central role in the operation of the computer. The substrate 12 also has a power connector 19 that receives power from the connector board 104. The hard disk device 11, the electronic circuit (I / O controller hub 15, memory controller hub 16, memory 17, CPU 18) on the substrate 12, and the air cooling fan 13 are each operated by power from the power connector 19. In FIG. 2, a power supply line to the air cooling fan 13 is denoted by reference numeral 20, and illustration of power supply lines to other components is omitted.

  Here, the I / O controller hub 15 and the memory controller hub 16 shown in FIG. 2 are, for example, about 45 mm long and about 50 mm wide. The four memories 17 shown in FIG. 2 are arranged in parallel so as to extend in the horizontal direction, for example, in a range of about 90 mm long × about 135 mm wide on the substrate 12. Further, the CPU 18 shown in FIG. 2 has a size of about 50 mm in length × about 50 mm in width, for example, and is arranged on the front side of the housing on the substrate 12. As an example, the heat generation amount of the memory 17 is 1032 kcal, and the heat generation amount of the CPU 18 is 5160 kcal.

  The air cooling fan 13 generates a cooling air flow in the casing 14 that is sucked from the opening 14 a on the front side of the casing and exhausted from the opening 14 b on the rear side of the casing. For example, three air-cooling fans 13 in one embodiment are arranged in the vertical direction on the rear side of the housing. Each air-cooling fan 13 is rotated by a double-axis motor (13a) incorporated in the rotation shaft of the fan. Of the three air-cooling fans 13, shafts (31, 41) are connected to the rotating shafts of the upper and lower air-cooling fans 13, respectively. The diameter of each fan shown in FIG. 2 is, for example, about 40 mm, and the horizontal length in the figure is about 50 mm.

  The liquid cooling unit is a device that cools the CPU 18 by circulating the cooling liquid. The liquid cooling unit includes a coolant flow path 21, a cooling plate 22, a radiator 23, a coolant tank 24, a first drive unit 25, and a second drive unit 26.

  The coolant channel 21 is connected in a loop on the substrate 12 via a cooling plate 22, a radiator 23 and a coolant tank 24. The coolant flow path 21 circulates coolant that serves as a coolant between the cooling plate 22, the radiator 23, and the coolant tank 24. Further, at a position below the housing, an extendable pump chamber 21a is formed, for example, in a liquid-tight manner between the radiator 23 of the coolant channel 21 and the coolant tank 24 (configuration of the pump chamber 21a). Will be described later).

  Here, the coolant channel 21 shown in FIG. 2 forms, for example, a substantially rectangular loop of about 200 mm in length and about 300 mm in width. The coolant channel 21 is formed of a copper pipe having an outer diameter φ of about 8 mm. In the cross section of the coolant channel 21, the shape of the space through which the coolant flows has a shape in which both ends of a vertically long rectangle are semicircular. The size of the space portion of the coolant channel 21 has a maximum width of about 3 mm and a maximum height of about 6 mm. The composition of the coolant is, for example, about 55% pure water and about 45% ethylene glycol. In FIG. 2, the flow of the coolant on the coolant channel 21 is indicated by solid line arrows.

  The cooling plate 22 is disposed so as to cover the upper side of the CPU 18 and is in thermal contact with the CPU 18. In the cooling plate 22, a plurality of coolant flow paths branched by a plurality of partitions are formed. Further, the plurality of flow paths in the cooling plate 22 merge in the cooling plate 22 and are connected to the coolant flow path 21. The heat generated by the CPU 18 is absorbed by continuously introducing the coolant from the coolant channel 21 side (hard disk device 11 side) before the cooling plate 22 into the channel of the cooling plate 22. Thereby, the CPU 18 can be cooled. The cooling plate 22 shown in FIG. 2 is made of copper and has a size of about 80 mm long × about 80 mm wide. In FIG. 2, the cooling plate 22 is shown in a cross section in order to show the flow path in the cooling plate 22.

  The radiator 23 is disposed on a coolant flow path 21 that extends in the vertical direction on the back side of the housing. The radiator 23 has a structure in which a plurality of heat radiating fins are attached so as to cover the outer periphery of the coolant channel 21. The cooling liquid in the high temperature state that has absorbed the exhaust heat from the CPU 18 by the cooling plate 22 is deprived of heat by passing through the flow path in the radiator 23. As a result, the coolant that has passed through the radiator 23 changes from a high temperature state to a low temperature state. The radiator 23 shown in FIG. 2 has a size of about 140 mm in length × about 40 mm in width.

  The coolant tank 24 is provided to replenish the coolant that is reduced by evaporation when the CPU 18 is cooled. The coolant tank 24 shown in FIG. 2 has a size of about 40 mm in length × about 45 mm in width.

  The first drive unit 25 transports the coolant in the coolant channel 21 using the power of the air cooling fan 13 on the upper side of the housing.

  FIG. 3 shows an example of the first drive unit 25 in an enlarged manner. The first drive unit 25 includes a shaft 31, a first rotation shaft 32, a second rotation shaft 33, and a screw shaft 34.

  The shaft 31 is connected to the rotating shaft of a double-axis motor 13a built in the air cooling fan 13 on the upper side of the housing. For example, the shaft 31 is a hollow tube, and the shaft 31 is connected to the rotating shaft of the biaxial motor 13a by inserting and fixing the rotating shaft of the biaxial motor 13a to the shaft 31. Note that the shaft 31 may be formed by extending the rotating shaft of the double-axis motor 13a.

  The first rotating shaft 32 extends in a direction substantially orthogonal to the shaft 31 and the second rotating shaft 33. Bevel gears (31 a, 32 a, 32 b, 33 a) are respectively provided at one end of the shaft 31 (opposite side of the air cooling fan 13), both ends of the first rotating shaft 32, and one end of the second rotating shaft 33. A bevel gear 31 a at one end of the shaft 31 meshes with a bevel gear 32 a at one end of the first rotation shaft 32. Further, the bevel gear 32 b at the other end of the first rotation shaft 32 is meshed with the bevel gear 33 a at one end of the second rotation shaft 33.

  A spiral rotating blade 34a is formed on the screw shaft 34 along the axial direction. For example, the screw shaft 34 is disposed in the coolant channel 21 over substantially the entire region of the coolant channel 21 on the upper side of the housing (see FIG. 2). The length of the screw shaft 34 is about 290 mm, for example. The diameter of the rotary blade 34a of the screw shaft 34 is, for example, about 3 mm. The pitch of the rotary blades 34a of the screw shaft 34 is about 5 mm.

  FIG. 4 shows an arrangement example of the screw shaft 34 in the coolant flow path 21. The rotating blade 34 a of the screw shaft 34 is disposed above the space portion of the coolant flow path 21.

  One end of the screw shaft 34 and the other end of the second rotating shaft 33 are connected by a non-contact joint of a magnet coupling 35 with a wall of the coolant channel 21 interposed therebetween.

  FIG. 5 shows an enlarged view of the magnet coupling 35 of the first drive unit 25. In FIG. 5, the screw shaft 34 and the second rotating shaft 33 are each supported by a bearing 36. The magnet coupling 35 is a joint that transmits torque without contact using magnetic force. In the magnet coupling 35, magnets 35a in which N poles and S poles are alternately arranged are provided on the driving side and the driven side. Torque is generated by operating the magnet coupling 35 with the drive side and driven side joints facing each other. The magnet shaft 35 is disposed at one end (driven side) of the screw shaft 34 and the other end (drive side) of the second rotating shaft 33, and the screw shaft 34 can be rotated by applying a force. In the magnet coupling 35, the torque can be adjusted by the number of magnetic poles of the N pole and the S pole. When the number of magnetic poles is small, the torque is high, and when the number of magnetic poles is large, the torque is low. In this embodiment, in order to circulate a low viscosity liquid, the number of magnetic poles of the magnet coupling 35 is, for example, 12 (N pole 6 and S pole 6), and the distance between the magnet couplings 35 is about 3 mm. For the magnet coupling 35, for example, MGC6008P-15SD / MGC6008P-15AD manufactured by B-Pro Inc. can be used.

  In the first drive unit 25, when the air cooling fan 13 on the upper side of the housing rotates, the shaft 31, the first rotating shaft 32, and the second rotating shaft 33 rotate by meshing of the bevel gears. And the screw shaft 34 connected with the 2nd rotating shaft 33 by the non-contact coupling (35) rotates with the rotational force of the air cooling fan 13. FIG. As a result, the coolant in the coolant channel 21 is transported by the rotation of the screw shaft 34.

  The second drive unit 26 converts the rotation of the air cooling fan 13 on the lower side of the housing into a linear motion, and expands and contracts the pump chamber 21a of the coolant channel 21 by the linear motion.

  FIG. 6 shows an example of the second drive unit 26 in an enlarged manner. The second drive unit 26 includes a shaft 41 and a shaft 42 with a cam.

  The shaft 41 is connected to the rotary shaft of a double-axis motor 13a built in the air cooling fan 13 on the lower side of the casing. For example, the shaft 41 is a hollow tube, and the shaft 41 is connected to the rotating shaft of the biaxial motor 13a by inserting and fixing the rotating shaft of the biaxial motor 13a to the shaft 41. Note that the shaft 41 may be formed by extending the rotating shaft of the double-axis motor 13a.

  The cam-equipped shaft 42 is disposed substantially orthogonal to the shaft 41. The cam-equipped shaft 42 is provided with a disc-shaped cam 42a. The shape of the disc of the cam 42a has an egg-shaped structure in which the distance from the rotation center of the shaft 42 to the outer periphery is different. Also, bevel gears (41a, 42b) are provided at one end of the shaft 41 (opposite side of the air cooling fan 13) and the other end of the cam-equipped shaft 42, respectively. The bevel gear 41 a at one end of the shaft 41 is meshed with the bevel gear 42 b at the other end of the shaft with cam 42. The cam 42a of the cam-equipped shaft 42 is in contact with the end of the pump chamber 21a in the expansion / contraction direction (the bottom surface of the pump chamber 21a).

  In the second drive unit 26, when the air cooling fan 13 on the lower side of the casing rotates, the shaft 41 and the cam-equipped shaft 42 rotate by meshing of the bevel gears.

  FIG. 7 shows an example of a state change of the cam 42a due to the rotation of the cam-equipped shaft 42. When the peripheral surface with a short distance from the rotation center of the cam 42a to the outer periphery passes through the pump chamber 21a due to the rotation of the cam-equipped shaft 42 (return stroke), the pump chamber 21a has an extension behavior (FIG. 7A). )). Further, when the peripheral surface having a long distance from the rotation center of the cam 42a to the outer periphery passes through the pump chamber 21a due to the rotation of the cam-equipped shaft 42 (the forward stroke), the pump chamber 21a becomes contracted (see FIG. 7). (B)).

  As shown in FIG. 7, when the cam 42 of the cam-equipped shaft 42 is formed so as to have different distances from the center of rotation, a reciprocating linear motion occurs. As a result, the rotation of the air cooling fan 13 can be converted into a linear movement in the expansion / contraction direction of the pump chamber 21a via the cam 42a. In addition, in FIG. 6, the state where the cam 42a is half-rotated from the solid line state and the extended state of the pump chamber 21a are indicated by broken lines.

  8 and 9 show a configuration example of the pump chamber 21a of the coolant channel 21. FIG. The pump chamber 21 a is formed of a copper bellows that is the same material as the pipe of the coolant channel 21. Further, the pump chamber 21a is fixed and integrated with the coolant channel 21 by welding or the like so that the coolant channel 21 and the pump chamber 21a are liquid-tight. The diameter of the pump chamber 21a is, for example, about φ24 mm, and the length of the pump chamber 21a in the horizontal direction in the drawing is about 20 mm.

  Further, in order to prevent the backflow of the coolant when the pump chamber 21a is expanded and contracted, the coolant flow path 21 is provided with a first check valve 51 and a second check valve 52 across the mounting position of the pump chamber 21a. Yes. The first check valve 51 is provided on the upstream side of the pump chamber 21a, and the second check valve 52 is provided on the downstream side of the pump chamber 21a. The first check valve 51 and the second check valve 52 have valve seats (51a, 52a), balls (51b, 52b), and stoppers (51c, 52c). The valve seat has an opening. The ball and the stopper are each arranged on the downstream side of the valve seat. The ball becomes a valve body that opens and closes the opening of the valve seat. The stopper serves to receive the ball on the downstream side.

  FIG. 8 shows the extended state of the pump chamber 21a. In the return stroke of the cam 42a, the bellows of the pump chamber 21a extends and the coolant is sucked into the pump chamber 21a. At this time, since the ball 51b of the first check valve 51 is pushed downstream by the flow of the coolant and is separated from the valve seat 51a, the first check valve 51 is opened. On the other hand, since the ball 52b of the second check valve 52 is sucked upstream to close the opening of the valve seat 52a, the second check valve 52 is closed. Therefore, the coolant flowing from the upstream side of the coolant flow path 21 flows into the pump chamber 21a.

  FIG. 9 shows the contracted state of the pump chamber 21a. In the advance stroke of the cam 42a, the bellows of the pump chamber 21a contracts and the coolant is discharged from the pump chamber 21a. At this time, the ball 51a of the first check valve 51 is pushed upstream to close the opening of the valve seat 51a, so that the first check valve 51 is closed. On the other hand, since the ball 52b of the second check valve 52 is pushed downstream by the flow of the coolant and is separated from the valve seat 52a, the second check valve 52 is opened. Therefore, the coolant discharged from the pump chamber 21a flows downstream without flowing backward to the upstream side.

  As described above, the expansion and contraction of the pump chamber 21a is repeated by the movement of the cam 42a, so that the coolant in the coolant channel 21 is transported.

  Hereinafter, the operation of the blade 102 according to the embodiment will be described. In the blade 102 according to an embodiment, the air cooling fan 13 rotates during operation, whereby a cooling air flow is generated in the casing 14 from the front side of the casing toward the rear side of the casing. With this air flow, the heat of the heat generating components (memory 17, CPU 18, etc.) in the blade 102 and the heat of the radiator 23 are exhausted outside the housing 14.

  In one embodiment, the screw shaft 34 is rotated by the first drive unit 25 according to the rotation of the air cooling fan 13, and the pump chamber 21 a is expanded and contracted by the second drive unit 26. Thereby, the coolant circulates in the coolant channel 21. The coolant in the coolant flow path 21 absorbs the heat of the CPU 18 from the cooling plate 22, then dissipates heat in the radiator 23 and returns to the cooling plate 22. Therefore, in the blade 102 of the embodiment, the CPU 18 is efficiently cooled also by the liquid cooling unit.

  In the liquid cooling unit according to the embodiment, the first driving unit 25 and the second driving unit 26 both transport the cooling liquid in the cooling liquid passage 21 by using the rotation of the air cooling fan 13 as power. Therefore, in one embodiment, since the electric pump for the coolant is not necessary, power consumption used for cooling the blade 102 can be suppressed.

  The first drive unit 25 according to the embodiment uses the magnet coupling 35 to transmit power to the screw shaft 34 disposed in the coolant channel 21 in a non-contact manner. Moreover, the 2nd drive part 26 of one Embodiment presses the pump chamber 21a formed liquid-tight, and conveys a cooling fluid. Therefore, according to the configuration of the first drive unit 25 and the second drive unit 26 described above, the coolant flow path 21 can be made into a closed space free from liquid leakage. It is reduced.

  In one embodiment, the cooling unit circulates the coolant using two drive units, the first drive unit 25 and the second drive unit 26. The power sources of the first drive unit 25 and the second drive unit 26 are different air cooling fans. Therefore, the cooling unit according to the embodiment can prevent the circulation of the coolant from stopping completely even if any of the first driving unit 25, the second driving unit 26, and the air cooling fan 13 is defective. it can.

<Description of Examples>
Example 1
In Example 1, in the configuration of the blade according to one embodiment, a job was run so that the CPU power consumption was 100 W, and the power consumption required for cooling was evaluated. At this time, the CPU temperature is 70 ° C. and the ambient temperature is 35 ° C. Cooling performance was evaluated using thermal resistance. When the thermal resistance is R (° C./W), the CPU temperature is Tcpu (° C.), the ambient temperature Tair (° C.), and the CPU power consumption is Q (W), R = (Tcpu-Tair) / Q. The thermal resistance in CPU cooling of 100 W is R = (70−35) /100=0.35° C./W, and when the thermal resistance is lower than this, it is determined that the CPU of 100 W has been cooled.

  The number of revolutions of the cooling fan can be changed by setting the power of the cooling fan. In order to utilize the rotational force of the cooling fan as a driving force source for the rotating blades and the pump chamber instead of using the pump for circulating the cooling liquid, in the first embodiment, the upper cooling fan serving as the power source for the first driving unit is used. The power was set to 7.2 W, the power of the central cooling fan was set to 6.0 W, and the power of the lower cooling fan serving as a power source for the second drive unit was set to 8.4 W. When the power setting of all the cooling fans is 6.0 W, the flow rate of the cooling liquid necessary for CPU cooling cannot be obtained, so the power of each cooling fan is set to a different value in order to secure a sufficient cooling liquid flow rate. did.

  Under the conditions of Example 1, the flow rate of the coolant in the coolant channel was 230 ml / min (actual value measured by a flow meter), and the CPU temperature was 68 ° C. The thermal resistance at this time was (68−35) /100=0.33, and it was found that the performance of sufficiently cooling the CPU was obtained. The power consumption required for cooling the blade in Example 1 is 21.6 W (7.2 W + 6.0 W + 8.4 W), and if the use for 24 hours a day is continued for one year, the annual power consumption is 189.2 kWh. Become.

(Example 2)
In Example 2, the power consumption required for cooling was evaluated in the blade configuration of one embodiment under the same conditions as in Example 1 except that the power of the upper cooling fan was set to 8.4 W.

  Under the conditions of Example 2, the coolant flow rate in the coolant channel was 310 ml / min (actually measured with a flow meter), and the CPU temperature was 66 ° C. The thermal resistance at this time was (66−35) /100=0.31, and it was found that the performance of sufficiently cooling the CPU was obtained. The power consumption required for cooling the blade in Example 2 is 22.8 W (8.4 W + 6.0 W + 8.4 W), and if the use for 24 hours a day is continued for one year, the annual power consumption is 199.7 kWh. Become.

(Comparative example)
As a comparative example of Example 1 and Example 2 described above, the power consumption required for cooling was evaluated using a blade using an electric pump for circulation of the coolant (the illustration of the blade of the comparative example is omitted). ). In the comparative example, the power of the three fans was set to 6.0 W, and the power of the electric pump was set to 6.0 W.

  Under the conditions of the comparative example, the flow rate of the coolant in the coolant channel was 230 ml / min (actual value measured with a flow meter), and the CPU temperature was 68 ° C. When the thermal resistance at this time is calculated, (68−35) /100=0.33, and it can be determined that the CPU is sufficiently cooled. Moreover, the power consumption required for cooling the blade of the comparative example is 24 W (6.0 W + 6.0 W + 6.0 W + 6.0 W), and if the use for 24 hours a day is continued for one year, the annual power consumption is 210.2 kWh. It becomes.

  Therefore, it can be seen that the configuration of Example 1 can reduce the annual power consumption by 21.0 kWh (= 210.2 kWh-189.2 kWh) as compared with the comparative example. Moreover, it turns out that the structure of Example 2 can reduce the power consumption in an year 10.5 kWh (= 210.2 kWh-199.7 kWh) rather than a comparative example.

  In the configuration of the comparative example, when the flow rate of the cooling liquid is made equal to the same amount (310 ml / min) as in Example 2, the annual power consumption is 219.0 kWh (the electric pump power is set to 7.0 W). It becomes. At this time, comparing Example 2 and the comparative example, it can be seen that the configuration of Example 2 can reduce the annual power consumption by 19.3 kWh (= 219.0 kWh-199.7 kWh) compared to the comparative example.

<Supplementary items of the embodiment>
(1) In the blade 102 of the above embodiment, the example in which the coolant transport mechanism by the screw shaft 34 is provided on the upper side of the casing and the coolant transport mechanism by expansion and contraction of the pump chamber 21a is provided on the lower side of the casing has been described. The configuration of the above embodiment is merely an example.

  FIG. 10 shows another configuration example of the blade in the embodiment. In the blade 102a shown in FIG. 10, the same components as those in the blade of FIG. In the example of FIG. 10, the first drive unit 25 and the screw shaft 34 are arranged instead of the second drive unit 26 and the pump chamber 21a of FIG. That is, the blade 102a shown in FIG. 10 is provided with a coolant transport mechanism (first drive unit 25) by the screw shaft 34 on the upper side and lower side of the case.

  As another example, a coolant transport mechanism by expansion and contraction of the pump chamber 21a may be provided on the upper side of the casing, and a coolant transport mechanism by the screw shaft 34 may be provided on the lower side of the casing (the blade 102 in this case) (The illustration is omitted). Alternatively, a coolant transport mechanism by extending and contracting the pump chamber 21a may be provided on the upper and lower sides of the casing (the illustration of the blade 102 in this case is omitted).

  Here, the amount of power consumption used for cooling is the smallest when two coolant transport mechanisms by the screw shaft 34 are provided. Further, when the cooling liquid transport mechanism by the screw shaft 34 and the cooling liquid transport mechanism by the expansion and contraction of the pump chamber 21a are combined, the amount of power consumption is larger than when two cooling liquid transport mechanisms by the screw shaft 34 are provided. Slightly bigger. Further, when two cooling liquid transport mechanisms by expansion and contraction of the pump chamber 21a are provided, the consumption of the cooling liquid is compared with a combination of the cooling liquid transport mechanism by the screw shaft 34 and the cooling liquid transport mechanism by expansion and contraction of the pump chamber 21a. The amount of power is slightly increased.

  (2) In the above embodiment, the example in which the electronic device cooling device is mounted on the blade 102 of the blade server 100 has been described. However, the electronic device cooling device may be another electronic device (for example, UNIX (registered trademark)). It can be widely applied to the configuration of a stationary computer such as a server). In addition, it is also effective as one embodiment to distribute the electronic device cooling device in a state in which the electronic device cooling device is incorporated in a housing of the electronic device before the circuit board is mounted.

  (3) In the above-described embodiment, the example in which the second driving shaft 33 and the screw shaft 34 are connected by the magnet coupling 35 in the first driving unit 25 has been described. However, as another example of the above-described embodiment, a seal bearing is disposed on the wall of the coolant flow path 22, and one end of the screw shaft 34 is inserted into the seal bearing so that the screw shaft 34 is inserted into the wall of the coolant flow path 22. It is good also as a structure penetrated.

  (4) In the above-described embodiment, the example in which the first driving unit 25 transports the coolant by rotating the screw shaft 34 in which the rotary blades 34a are spirally formed has been described. However, as another example of the above embodiment, for example, a configuration in which the blades of the spiral pump and the gear of the gear pump are rotated by the rotational force of the air cooling fan 13 may be adopted.

  (5) The structure of the 2nd drive part 26 is not limited to the example of the said embodiment, For example, you may convert rotation of the air-cooling fan 13 into a linear motion using a slider crank mechanism.

  From the above detailed description, features and advantages of the embodiments will become apparent. It is intended that the scope of the claims extend to the features and advantages of the embodiments as described above without departing from the spirit and scope of the right. Further, any person having ordinary knowledge in the technical field should be able to easily come up with any improvements and modifications, and there is no intention to limit the scope of the embodiments having the invention to those described above. It is also possible to use appropriate improvements and equivalents within the scope disclosed in.

DESCRIPTION OF SYMBOLS 11 ... Hard disk drive; 12 ... Board | substrate; 13 ... Air-cooling fan; 13a ... Dual-axis motor; 14 ... Housing | casing; 14a, 14b ... Opening; 15 ... I / O controller hub; ... CPU; 19 ... Power connector; 20 ... Power supply line; 21 ... Coolant flow path; 21a ... Pump chamber; 22 ... Cooling plate; 23 ... Radiator; 24 ... Coolant tank; 25 ... First drive part; 32, first rotating shaft; 33, second rotating shaft, 34, screw shaft; 34a, rotating blade, 35, magnet coupling, 35a, magnet, 36, bearing; ... Shaft with cam; 42a ... Cam; 31a, 32a, 32b, 33a, 41a, 42b ... Bevel gear; 51 ... First check valve; 52 ... Second check valve; 2a ... valve seat; 51b, 52 b ... ball; 51c, 52c ... stopper; 100 ... blade servers; 101 ... chassis; 102, 102a ... blade; 103 ... power supply unit; 104 ... connector board

Claims (5)

An air-cooling fan that cools the heat-generating parts of the electronic device,
A coolant flow path through which a coolant for cooling the heat generating component flows;
Using the power of the air cooling fan, a drive unit for transporting the coolant in the coolant channel;
A cooling device comprising: The cooling device according to claim 1, wherein
The drive unit is
A joint for transmitting rotation of the air cooling fan;
A rotating blade arranged in the coolant flow path and rotated by the rotational force of the air cooling fan transmitted through the joint to transport the coolant;
Including cooling system. The cooling device according to claim 2, wherein
The cooling device according to claim 1, wherein the joint is a non-contact joint. In the cooling device of the electronic device of any one of Claims 1-3,
The cooling fluid passage is formed with an extendable pump chamber,
The drive unit is a cooling device for an electronic device that transports the coolant by expanding and contracting the pump chamber by rotation of the air cooling fan. Heat-generating parts,
An air cooling fan for cooling the heat generating component;
A coolant flow path through which a coolant for cooling the heat generating component flows;
Using the power of the air cooling fan, a drive unit for transporting the coolant in the coolant channel;
Electronic equipment comprising.

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