JP2009260371A - Electronic-component cooling device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact water-cooled electronic-component cooling device. <P>SOLUTION: The electronic-component cooling device is constituted of a so-called water-cooled heat sink 3, a radiator 7 cooled by an electric fan 5, a first and a second refrigerant channels 9, 11 to circulate the refrigerant in between the heat sink 3 and the radiator 7, and an electric pump 13 to feed a moving energy to the refrigerant. The electric pump 13 is disposed in face to face with the dissipating unit of the radiator 7. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an electronic component cooling device for forcibly cooling electronic components such as a microcomputer, and an electric pump and a heat sink used in the electronic component cooling device.

  As shown in US Pat. No. 5,519,574, a conventional electronic component cooling apparatus includes a heat sink having a plurality of heat radiation fins on the surface of a base plate, and an electric motor that forcibly cools the surfaces of the plurality of heat radiation fins and the base plate. Most of them consisted of fans.

US Pat. No. 5,519,574

  However, when the heat generation amount of the electronic component increases, there arises a problem that the electronic component cannot be cooled to a necessary and sufficient level by simply cooling the heat sink with air.

  An object of the present invention is to provide an electronic component cooling apparatus capable of cooling an electronic component having a large calorific value to a necessary and sufficient level by so-called water cooling.

  Another object of the present invention is to provide a small water-cooled electronic component cooling apparatus.

  Another object of the present invention is to provide an electronic component cooling apparatus which is small and has high cooling performance.

  Still another object of the present invention is to provide an electronic component cooling device in which an electric fan can be easily attached to a radiator.

  Another object of the present invention is to provide an electronic component cooling device in which a fan guard can be easily attached.

  Another object of the present invention is to provide an electronic component cooling apparatus in which a fan guard can be easily and reliably attached.

  Another object of the present invention is to provide an electronic component cooling device and a heat sink that can improve the cooling performance without increasing the size of the heat sink.

  Another object of the present invention is to provide an electronic component cooling device capable of suppressing a temperature rise of an electric pump.

  Another object of the present invention is to provide an electronic component cooling apparatus that does not require a reserve tank.

  Still another object of the present invention is to provide an electronic component cooling apparatus including a radiator in which air is not easily mixed in a circulating refrigerant.

  Another object of the present invention is to provide an electronic component cooling apparatus including a radiator that is not damaged even when the temperature changes.

  Another object of the present invention is to provide an electronic component cooling device in which a tube for piping is simply and firmly connected, and the tube bending operation is easy.

  Still another object of the present invention is to provide an electronic component cooling apparatus that can be easily maintained.

  Still another object of the present invention is to provide an electronic component cooling apparatus capable of reliably mounting a gasket.

  Another object of the present invention is to provide an electric pump suitable for use in an electronic component cooling apparatus.

  Another object of the present invention is to provide an electric pump capable of discriminating an operation state.

  Still another object of the present invention is to provide an electric pump capable of performing pump operation without any trouble without being affected by dust and bubbles.

  Still another object of the present invention is to provide an electric pump that is not affected by dust and bubbles and that consumes less power.

  The present invention includes a heat sink that is cooled by a refrigerant and cools an electronic component such as a CPU, a radiator that cools the refrigerant, an electric fan that cools the radiator, and an electric pump that circulates the refrigerant as main components. Targets water-cooled electronic component cooling devices. The heat sink includes an electronic component mounting surface on which an electronic component to be cooled is mounted, a coolant inlet and a coolant outlet, and a coolant channel through which a liquid as a coolant for forcibly cooling the electronic component mounting surface flows. ing. The radiator includes a liquid inlet and a refrigerant outlet and a liquid channel through which the refrigerant flows, and the liquid channel is cooled by air cooling to cool the refrigerant. The electric fan is attached to the radiator of the radiator and cools the radiator of the radiator by generating air cooling air by the rotation of the impeller provided with a plurality of blades. Typically, the electric fan sucks air from the heat radiating portion side of the radiator to cool the heat radiating portion.

  The electric pump supplies the refrigerant flowing out from the refrigerant outlet of the radiator to the refrigerant inlet of the heat sink, and gives the moving energy to supply the refrigerant flowing out of the refrigerant outlet of the heat sink to the refrigerant inlet of the radiator.

  In this invention, an electric pump is arrange | positioned in the position facing the impeller non-opposing area | region of a thermal radiation part different from the impeller opposing area | region facing the impeller of the thermal radiation part of a radiator. In order to maximize the function of the radiator for cooling the refrigerant, it is common knowledge of those skilled in the art to place an object that obstructs the flow of the cooling air generated by the rotation of the electric fan in front of the radiator heat dissipation part. Judging from that, it is something that must be avoided. However, in the present invention, this common sense is deliberately broken, and the electric pump is arranged in the non-opposing region where the impeller is not opposed to the front region of the radiator heat dissipating part. As a result, it is expected that the cooling performance is slightly lowered as compared with the case where the electric pump is not disposed in front of the heat radiating portion. However, since the electric pump can be disposed in the planar shape of the radiator, the overall size of the electronic component cooling device in the planar shape can be reduced without greatly reducing the cooling performance. In order to ensure the required cooling performance, the size of the impeller non-opposing region of the heat radiating portion may be set to an appropriate size.

  The electric fan includes an electric motor that rotates the impeller and a housing. The housing includes a wind tunnel portion and a duct forming wall portion. The wind tunnel portion has a suction port at one end facing the impeller facing region of the heat radiating portion of the radiator, and a discharge port at the other end. The duct forming wall portion is provided continuously with the wind tunnel portion, and is configured to guide the air emitted from the impeller non-opposing region of the heat radiating portion to the suction port. If such a duct forming wall portion is provided, the cooling air can be drawn out from the impeller non-opposing region that does not directly face the impeller, so that the heat radiating portion of the radiator can be cooled almost entirely. In this case, an opening for exposing the heat generating portion of the electric pump is formed in the duct forming wall portion of the housing. And what is necessary is just to arrange | position an electric pump in the state which exposed the heat generating part of the electric pump from this opening part. If it does in this way, the heat which generate | occur | produces from an electric pump will be thermally radiated outside a housing, and it can prevent that the thermal radiation performance of a radiator is influenced.

  The electric pump may be arranged anywhere as long as it is in the impeller non-opposing region. However, in particular, it is preferable to dispose the electric pump adjacent to one corner of the radiator radiating section. Because the electric pump is least likely to be an obstacle to the flow of cooling air, it has the least effect on the cooling performance of the radiator or on the fan noise (wind noise) Because it can be.

  Further, in order to facilitate attachment of the electric fan to the radiator, the following is preferable. For example, a plurality of engagement pieces are integrally provided on the housing. The radiator is provided with a plurality of engaged portions that engage with the plurality of engaging pieces and attach the housing to the radiator. If it does in this way, an electric fan can be easily attached to a radiator, without using a screw etc.

  An operation state display means for displaying that the electric pump is operating may be provided in the outer case of the electric pump exposed from the opening provided in the housing of the electric fan. As the operation state display means, it is preferable to provide light emission display means such as a light emitting diode. The electric fan can immediately determine whether the electric fan is normal or abnormal by observing the rotation state of the impeller. On the other hand, the electric pump cannot see the operation part from the outside. Therefore, when the operation state display means is provided, the operation of the electric pump can be confirmed from the outside of the electric fan, so that the confirmation work at the time of inspection and repair becomes easy.

  Moreover, it is preferable to form a plurality of heat radiating through holes for releasing heat generated from the heat generating portion of the driving motor disposed inside the exterior case of the electric pump exposed from the opening. Providing such a plurality of heat radiating through holes makes it possible to radiate most of the heat generated from the electric pump out of the housing of the electric fan. As a result, the influence of heat applied from the electric pump to the radiator can be reduced. Moreover, since the temperature of the electric pump can be lowered, the influence of heat applied from the electric pump to the refrigerant passing through the electric pump can be reduced.

  It is preferable that the fan guard can be attached to the outlet of the wind tunnel portion of the electric fan through a detachable mounting structure. A fan guard is not always necessary. However, if the fan guard is detachable, the fan guard can be attached according to the customer's request, so the versatility is enhanced.

  The structure of the fan guard is arbitrary. In order to facilitate attachment to the wind tunnel, a structure including a guard portion facing the discharge port, and a plurality of snap-in type hooks provided on the outer periphery of the guard portion at intervals in the circumferential direction Is preferable. In this case, a plurality of engaged portions to which a plurality of hooks are snap-in coupled are integrally provided on the outer peripheral portion of the wind tunnel portion of the electric fan. A mounting structure is constituted by the plurality of hooks and the plurality of engaged portions. Here, the snap-in coupling means that a coupling relationship is obtained in which the hook is bent or reduced and the hook is engaged with the engaged portion after the hook is bent over the engaged portion. It means a bond structure.

  In order to ensure the snap-in coupling, it is preferable to provide a contact portion that contacts the casing of the electric motor at the guard portion of the fan guard. The shape of the contact portion is such that the contact portion is in contact with the casing and the guard portion is bent so as to be closer to the discharge port in a state where a plurality of hooks are engaged with a plurality of engaged portions. Determine to be. If it does in this way, a hook can be strongly pressed to an to-be-engaged part by the bending of a guard part, and a snap-in coupling | bonding can be ensured.

  In addition, it is preferable that a plurality of stopper portions that are provided closer to the housing than the plurality of engaged portions and are in contact with the tip portions of the plurality of hooks are integrally provided on the outer peripheral portion of the wind tunnel portion. Providing such a stopper can prevent the hook from being pushed too far and the guard to bend more than necessary and break the guard.

  The structure of the heat sink to be used is arbitrary. A preferable heat sink includes a base plate, a top plate, and a peripheral wall portion connecting the base plate and the top plate. The base plate includes an electronic component mounting surface and a heat radiating surface that is opposed to the electronic component mounting surface in the thickness direction and is in direct contact with the refrigerant. The top plate includes a facing surface that faces the heat radiating surface of the base plate with a predetermined gap therebetween. The peripheral wall connects the base plate and the top plate so as to form a chamber between the base plate and the top plate. A preferred heat sink includes a partition wall that partitions the chamber. The partition wall portion is coupled or closely adhered to one of a pair of peripheral wall constituent portions opposed to the circumferential wall portion, extends toward the other, and is coupled or adhered to both the base plate and the top plate. Due to the presence of the partition wall portion, first and second divided chambers are formed on both sides of the partition wall portion in the chamber, and the first and second chambers are formed between the partition wall portion and the other of the pair of peripheral wall components. A communication passage that communicates the divided chambers is formed. The refrigerant inlet of the heat sink is provided so as to communicate with the first chamber partial region located on the opposite side of the communication path of the first divided chamber. The refrigerant outlet of the heat sink is provided so as to communicate with the second chamber partial region located on the opposite side of the communication path of the second divided chamber. By doing so, the refrigerant inlet and the refrigerant outlet of the heat sink will be placed close to each other, making it easy to connect the pipe to the heat sink, and the presence of the pipe will be an obstacle to fixing the heat sink Less. In the first and second divided chambers, a plurality of radiating fins provided at least so as to be able to transfer heat to the base plate are arranged so as not to prevent the refrigerant from flowing. The refrigerant that has entered the first divided chamber from the refrigerant inlet comes into contact with the plurality of radiating fins in the first divided chamber, and then enters the second divided chamber through the communication path. After coming into contact with the plurality of radiating fins, the refrigerant is discharged from the refrigerant outlet. With such a structure, the cooling performance is improved without increasing the shape of the heat sink. The reason is that the ratio of the width dimension of the first divided chamber and the second divided chamber to the diameter dimension of the refrigerant inlet and the refrigerant outlet does not become so large, so that the gap between the plurality of radiating fins in each chamber is not increased. This is because there is no significant difference in the flow rate and flow rate of the flowing refrigerant, and heat transfer from each radiating fin to the refrigerant is performed without delay.

  The plurality of radiating fins can be constituted by a plurality of plate-shaped radiating fins extending side by side with the partition wall portion. In this case, a gap through which the refrigerant flows is formed between two adjacent plate-shaped heat radiation fins. What is necessary is just to determine the thickness of a plate-shaped heat radiation fin, and the width dimension of a gap | interval so that required cooling performance can be acquired. The base plate, the partition wall portion, and the plurality of plate-like heat radiation fins can be integrally formed. Further, the top plate and the peripheral wall portion are integrally formed. Then, the partition wall and the tips of the plurality of plate-shaped heat radiation fins are coupled or closely attached to the top plate. By adopting such a configuration, it is possible to obtain a heat sink capable of making the heat radiation area as large as possible with a small number of parts. In addition, when the tips of the plate-shaped radiating fins are joined and closely attached to the top plate, the refrigerant does not flow between the tip surface of the radiating fins and the top plate, and the circulation of the refrigerant is limited only to the gaps between the radiating fins. . As a result, it is possible to effectively prevent the amount of heat transfer from the heat radiating fins to the refrigerant, and to improve the cooling performance.

  If the refrigerant inlet and the refrigerant outlet of the heat sink are formed on the top plate, it is easy to connect the pipe to the heat sink, and the presence of the pipe rarely becomes an obstacle when fixing the heat sink. Here, the tube connecting cylinder may be connected to the refrigerant inlet and the refrigerant outlet formed on the top plate by soldering or brazing. In such a case, a flange having an annular space for receiving molten metal leaking from the refrigerant inlet or the refrigerant outlet to the surface side of the top plate is integrally formed on the outer peripheral portion on the base side of the tube connecting cylinder. It is preferable to provide it. When such a flange portion is provided on the tube connecting cylinder, the molten metal for soldering or brazing attached between the back surface of the top plate and the outer peripheral surface of the base of the tube connecting cylinder is formed on the top plate. It is possible to prevent leakage in a form that is visible from the outside on the surface side. Therefore, even if the tube connecting cylinder is attached to the top plate by soldering or brazing, the appearance of the heat sink is not impaired.

  The plurality of plate-shaped heat radiation fins are arranged at positions excluding the first chamber partial region and the second chamber partial region, and the third chamber partial region and the fourth chamber partial region sandwiching the communication path therebetween. . If the occupied volume of the heat radiating fins in the chamber is increased more than necessary, the flow rate of the refrigerant is decreased, and the cooling performance is deteriorated. When the first to fourth chamber partial regions are provided, it is possible to suppress a drastic decrease in the flow rate of the refrigerant even when the heat dissipating fins are provided in the chamber. Moreover, it is preferable to comprise the part of the inner wall surface of the surrounding wall part surrounding the four corners of a chamber by the curved surface which does not form a corner part. If it does in this way, the channel resistance in the corner in a chamber can be made small, and the fall of the flow velocity can be controlled.

  The structure of the electric pump to be used is arbitrary. A typical rotary electric pump includes an impeller that includes a plurality of radially extending blades and that rotates around an axis, and a housing that includes an impeller storage chamber therein. The housing includes a liquid inlet and a liquid outlet. The impeller storage chamber is configured such that when the impeller is immersed in the refrigerant and the impeller rotates, the refrigerant is sucked from the liquid inlet and discharged from the liquid outlet. The liquid inlet is formed in a wall portion facing the plurality of blades among the plurality of wall portions surrounding the impeller storage chamber so as to be positioned on the extension line of the axis. The liquid outlet is formed in a wall portion located in a direction orthogonal to the axis among the plurality of wall portions. In the electric pump having such a structure, an annular groove portion that opens toward the impeller side so as to completely surround the periphery of the liquid inlet is formed in the wall portion where the liquid inlet is formed, and an annular groove portion is formed outside the annular groove portion. It is preferable to form a plurality of elongated grooves that are formed so as not to be continuous with the grooves and extend radially around the axis and open toward the impeller. The shape and dimensions of the annular groove and the plurality of elongated grooves are such that dust and bubbles entering the impeller storage chamber from the liquid inlet are between the blades and the corners of the annular grooves and the elongated grooves. It is determined to be crushed, moved radially outward by centrifugal force along the elongated groove, and discharged from the liquid outlet. In this way, it is possible to effectively prevent dust and bubbles from remaining in the impeller storage chamber and lowering the pump performance. The annular groove may be omitted. Moreover, you may attach the taper which inclines so that it may approach gradually toward the wall part facing a some blade in the wall surface part located in the radial direction outer side among the wall surfaces surrounding an elongate groove part. In this way, bubbles, dust, and the like that have moved radially outward by centrifugal force are smoothly discharged from the elongated groove portion without being caught by the edge of the elongated groove portion. Further, compared with the case where no taper is provided, loss when the impeller is rotated is reduced, and power consumption can be reduced.

  The plurality of elongated grooves are preferably formed at equal intervals in the circumferential direction. In this way, the presence of these elongated grooves does not cause uneven rotation of the impeller.

  The impeller rotational driving method is arbitrary. For example, a plurality of permanent magnet magnetic poles are arranged on the impeller so as to be arranged around the axis. And the several permanent magnet magnetic pole for a drive rotated by the electric motor for a drive of an electric pump is arrange | positioned in the position facing a several permanent magnet magnetic pole via a partition. The permanent magnet magnetic pole and the driving permanent magnet magnetic pole may be opposed in the axial direction of the impeller axis, or may be opposed in the radial direction orthogonal to the axial direction. If it does in this way, an impeller can be rotated using the magnetic attraction force which generate | occur | produces between several permanent magnet magnetic poles for a drive, and several permanent magnet magnetic poles. With this structure, waterproofing of the electric motor for driving the electric pump can be easily realized.

  As for the radiator to be used, what has the structure where the thermal radiation part was arrange | positioned between the upper side tank and the lower side tank is common. In this case, when the direction from the electric fan toward the radiator is the thickness direction of the radiator, it is preferable to make the dimensions in the thickness direction of the upper tank and the lower tank larger than the dimensions in the thickness direction of the heat radiating portion. When such a configuration is adopted, the upper tank and the lower tank can be made to function as a reservoir tank for storing a spare refrigerant for replenishing the evaporated refrigerant. In this case, the capacity of the upper tank is preferably larger than the capacity of the lower tank. To say how much the capacity is increased, the capacity of the upper tank is made larger than the capacity of the lower tank so that an air space compressed during expansion of the refrigerant is formed in the upper tank. If such an air space can be secured, even when the outside air temperature rises and the refrigerant expands, it is possible to prevent the occurrence of an accident in which the internal pressure of the radiator is excessively increased and the radiator is damaged.

  It is preferable to further provide an inlet side extension pipe portion extending from the refrigerant inlet of the radiator into the upper tank or the lower tank and an outlet side extension pipe portion extending from the refrigerant outlet of the radiator into the upper tank or the lower tank. In this case, the inlet side extension pipe part and the outlet side extension pipe part are arranged so that the terminal opening is always located inside the refrigerant regardless of the posture of the radiator. In this way, air can be effectively prevented from entering the inlet side extension pipe part and the outlet side extension pipe part regardless of whether the upper tank or the lower tank has air. As a result, the rate at which air is supplied into the electric pump and the performance of the electric pump is degraded and the cooling performance is degraded can be greatly reduced.

  In addition, mounting brackets that are used when the upper tank and the lower tank are each attached to a portion to be attached (for example, a frame of a computer casing) may be integrally provided. Providing such a mounting bracket makes it very easy to mount the radiator, which is the heaviest, on the mounted portion. The structure of the mounting bracket is arbitrary. For example, a first mounting bracket that constitutes a hinge mechanism in a state in which the mounting bracket is mounted on the mounted portion, and a second mounting bracket that is fixed to the mounted portion using a fixing means such as a screw or a bolt It can consist of In this case, the first mounting bracket provided in the upper tank and the first mounting bracket provided in the lower tank are arranged so as to be aligned in the vertical direction. Similarly to the first mounting bracket, the second mounting bracket may be arranged so as to be aligned in the vertical direction, but the arrangement position thereof is arbitrary. When such first and second mounting brackets are used, the first mounting bracket can be used even when the radiator is not completely removed from the mounted portion during the maintenance of the equipment employing the electronic component cooling apparatus of the present invention. If the radiator is rotated around the hinge mechanism constituted by the above, it is possible to inspect and replace various parts located in front of the radiator. Therefore, the presence of a large radiator does not interfere with maintenance.

  Therefore, for example, the first mounting bracket can be composed of two pin-shaped mounting brackets arranged at an interval in the thickness direction. In this case, the mounted part is composed of two pin-shaped mounting brackets so that the other pin-shaped mounting bracket rotates within a predetermined angle range around one pin-shaped mounting bracket. What is necessary is just to make it the structure which hold | maintains a metal fitting. The second mounting bracket may have a structure in which a hole through which a screw or a bolt passes is formed. In this way, the radiator can be easily attached and rotated.

  It is preferable to enclose the refrigerant in a pressure state lower than the atmospheric pressure inside the system including the radiator (path through which the refrigerant circulates). In this way, even if the outside air temperature rises and the refrigerant pressure rises, the refrigerant pressure can only rise to a pressure that does not damage the system.

  Further, generally, tube connecting cylinders extending outward are respectively provided at the fluid inlet and the fluid outlet of the radiator, the refrigerant inlet and the refrigerant outlet of the heat sink, and the liquid inlet and the liquid outlet of the pump. In this case, both ends of the tube having flexibility are fitted to the outer peripheral portions of the corresponding two tube connecting cylinders. Therefore, the outer periphery of these tube connecting cylinders is tapered so that a taper surface whose diameter increases from the distal end toward the base and an edge that bites into the inner wall of the tube is formed between the tapered surface. It is preferable to provide one or more edge forming protrusions having an edge forming surface extending from the top of the surface toward the tube connecting cylinder. When one or more of such edge forming protrusions are provided, the edge of the edge forming protrusion can be caused to bite into the inner wall of the tube in the process of fitting the tube to the tube connecting cylinder. It is possible to firmly stop. Therefore, the hose band for preventing the slip that has been conventionally required becomes unnecessary. In addition, the edge of the edge forming protrusion provided on the tube connecting tube bites into the inner wall of the tube, so there is no gap between the two, greatly reducing liquid leakage or liquid evaporation at the connecting portion. be able to. The tube is preferably made of a material that is excellent in heat resistance, chemical resistance, and weather resistance and does not have much flexibility and stretchability. As a currently preferable tube, a plastic tube is preferable, and a tube formed of a fluororesin is particularly preferable. In addition, even if it is formed of a fluororesin, if a tube formed of a fluororesin having a lower water permeability is used, it is possible to suppress the refrigerant from passing through the outer wall portion of the tube and reducing the refrigerant. A spiral groove or a bellows-like groove extending in the longitudinal direction of the tube is formed in the outer peripheral portion of the main portion of the tube. If such a groove is formed, even when the tube does not have flexibility or stretchability, the bending work when attaching the heat sink becomes easy.

  The radiator is fixed to the mounted part through a gasket made of an elastic material such as sponge or rubber between the outer peripheral edge of the surface located on the side not facing the electric fan of the radiator and the mounted part, and sealed. May increase sex. However, if the gasket is affixed at an appropriate position, the deformed gasket comes into contact with the heat radiating surface of the heat radiating portion, and the air inflow area to the heat radiating portion is reduced, which may reduce the cooling performance. Further, depending on the deformation mode of the gasket, the adhesion with the attached portion may be deteriorated, and the sealing performance may be deteriorated. Therefore, in order to solve such a problem, the radiator is supported in a state where the gasket is separated from the heat radiating portion, and when the elastic material is pressed toward the mounting portion, the gasket is in a stable state on the mounting portion. It is preferable to attach a gasket support member that restricts deformation of the elastic material so as to be in close contact. If the gasket is supported using such a gasket support member, the gasket is not attached at a position that affects the cooling performance. Further, since the gasket can always be deformed in a predetermined shape, it is possible to prevent a decrease in sealing performance. The gasket support member is preferably detachably attached to the radiator. This is because it may not be necessary to use a gasket depending on the mode of use.

It is a perspective view of an example of an embodiment of an electronic component cooling device of the present invention. It is a block which shows the flow-path structure of embodiment of FIG. It is a front view of embodiment of FIG. It is a rear view of embodiment of FIG. FIG. 2 is a right side view of the embodiment of FIG. 1. It is a left view of embodiment of FIG. It is a top view of embodiment of FIG. It is a bottom view of embodiment of FIG. (A) And (B) is the front view and back view of an electric fan. It is a figure which shows the attachment state of an electronic component cooling device. It is a front view of a radiator. (A) is a right side view of the radiator, (B) is a cross-sectional view taken along line BB of FIG. 12 (A). It is a side view of a fingered. (A) And (B) is a figure used in order to demonstrate the attachment state of a fingered. It is the perspective view which looked at the electric pump from the back side. It is the perspective view which looked at the electric pump from the front side. It is a side view of an electric pump. It is a rear view of an electric pump. It is a BB schematic sectional drawing of FIG. It is a figure which shows the state made into the cross section in the position of the AA line of FIG. It is CC sectional schematic sectional drawing of FIG. It is a longitudinal cross-sectional view of the other example of an electric pump. It is a figure which shows the structure of the wall part in which the liquid inlet_port | entrance of the electric pump was formed. It is an expanded sectional view of the principal part of FIG. It is a perspective view of a heat sink. It is a top view of a heat sink. It is a front view of a heat sink. It is the sectional view on the AA line of FIG. It is the BB sectional drawing of FIG. It is CC sectional view taken on the line of FIG. It is an expanded sectional view of the state which connected the tube to the cylinder for tube connection. (A) thru | or (F) has shown the left view, front view, bottom view, top view, right view, and back view of the electronic component cooling device which attached the gasket. (A) thru | or (C) is sectional drawing used for the front view of a gasket holder, a right view, and description of a gasket holder.

  Hereinafter, an example of an embodiment of an electronic component cooling device of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a perspective view of an example of an embodiment of an electronic component cooling device 1 according to the present invention, and FIG. 2 is a block showing a flow path configuration of this embodiment. 3 to 8 are a front view, a rear view, a right side view, a left side view, a plan view, and a bottom view of this embodiment. FIG. 9A is a front view of the electric fan 5, and FIG. 9B is a rear view of the electric fan 5. 11 and 12 are a front view and a right side view of the radiator.

  As shown in FIGS. 1 to 8, the electronic component cooling apparatus 1 includes a water-cooled heat sink 3 having a so-called refrigerant flow path, a radiator 7 cooled by an electric fan 5, a heat sink 3, and a radiator 7. And an electric pump 13 that gives kinetic energy to the refrigerant in order to circulate the refrigerant between them. As will be described in detail later, the heat sink 3 includes an electronic component mounting surface 31a on which an electronic component 4 to be cooled, such as a CPU, is mounted, a refrigerant inlet (a portion to which the tube connecting cylinder 35 is connected), and a refrigerant outlet. (A portion to which the tube connecting cylinder 36 is connected) and a refrigerant flow path through which a liquid as a refrigerant for forcibly cooling the electronic component mounting surface flows. The radiator 7 has a refrigerant inlet 80 and a refrigerant outlet 81 and includes a liquid channel through which the refrigerant flows. The radiator 7 is cooled by air to cool the refrigerant. The electric fan 5 has an impeller 51 that is attached to a heat radiating portion of the radiator 7 and includes a plurality of blades 50. As the impeller 51 rotates, cooling air is attracted from the radiator 7 side to cool the radiator 7. The first refrigerant passage 9 composed of a tube for piping connects the refrigerant outlet 36 of the heat sink 3 and the refrigerant inlet 80 of the radiator 7. The second refrigerant passage 11 having the electric pump 13 on the way is configured to connect the refrigerant outlet 81 of the radiator 7 and the refrigerant inlet 35 of the heat sink 3.

  The electric pump 13 supplies the refrigerant flowing out from the refrigerant outlet 81 of the radiator 7 to the refrigerant inlet 35 of the heat sink 3, and supplies the refrigerant flowing out of the refrigerant outlet 36 of the heat sink 3 to the refrigerant inlet 80 of the radiator 7. To give.

  As shown in FIGS. 9A and 9B, the electric fan 5 includes an electric motor 52 that rotates the impeller 51 and a housing 53. The housing 53 includes a wind tunnel portion 54 and a duct forming wall portion 55. In the present embodiment, as shown in FIG. 11, the electric pump is located at a position facing the impeller non-facing region 73 of the heat radiating portion 71 different from the impeller facing region 72 of the heat radiating portion 71 of the radiator 7 facing the impeller 51. 13 is arranged. Specifically, as seen in the plan view shown in FIG. 3, the electric pump 13 is disposed adjacent to the upper right corner, which is one corner of the heat radiating portion 71 in the radiator 7.

  As shown in FIGS. 3 to 8 and FIGS. 10 to 12, the outer walls of the upper tank 74 and the lower tank 75 of the radiator 7 are respectively attached to attached portions (for example, a frame of a computer casing). A second mounting provided with a first mounting bracket composed of a pair of pin-shaped mounting brackets 78a and 78b and 79a and 79b, and holes 78d and 79d through which screws or bolts constitute a mounting bracket used when The metal fittings 78c and 79c are integrally provided. The pair of pin-shaped mounting brackets 78a and 78b and the pair of pin-shaped mounting brackets 79a and 79b constituting the first mounting bracket are aligned in the vertical direction. The second mounting brackets 78c and 79c are also aligned in the vertical direction.

  As shown in FIG. 10, the first mounting bracket made up of a pair of pin-shaped mounting brackets 78a and 78b and 79a and 79b is composed of a pair of plastic support portions 101 on the mounted portion side (support portions located on the lower side). (Not shown) constitutes a hinge mechanism. Two grooves 102 and 103 are formed in the support portion 101. A pin-shaped mounting bracket 78 b is fitted into the groove 102, and a pin-shaped mounting bracket 78 a is fitted into the groove 103. The radiator 7 swings by sliding the pin-shaped mounting brackets 78a and 79a in the groove 103 around the pin-shaped mounting brackets 78b and 79b. As a result, even after the radiator 7 is attached, the electric fan 5 and the electric pump 13 can be easily inspected and the maintenance inside the attached housing can be easily performed. The second mounting brackets 78c and 79c are fixed to the supporting portion 104 on the mounted portion side using screws 105.

  As shown in FIG. 11, a screw hole 77 for attaching the electric pump 13 using a screw is formed in the side wall portion of the upper tank 74 of the radiator 7. A refrigerant inlet 106 is provided on the side wall of the upper tank 74. The refrigerant is injected into the upper tank 74 from the refrigerant inlet 106, and after the injection, the refrigerant inlet 106 is closed by welding. The pressure of the refrigerant in the refrigerant circulation system is set to be lower than the atmospheric pressure. The pressure of the refrigerant is determined so that the pressure does not become extremely higher than the atmospheric pressure even when the refrigerant expands due to a temperature rise and the pressure rises. Therefore, even if the outside air temperature rises and the refrigerant pressure rises, the refrigerant pressure does not damage the refrigerant circulation system.

  As shown in FIGS. 5, 6, and 12 (A), when the direction from the electric fan 5 toward the radiator 7 is the thickness direction of the radiator 7, the upper tank 74 and the dimension in the thickness direction of the heat radiating portion 71 and The size of the lower tank 75 in the thickness direction is increased. When such a configuration is adopted, the upper tank 74 and the lower tank 75 can function as a reservoir tank for storing a spare refrigerant for replenishing the evaporated refrigerant. In the present embodiment, the capacity of the upper tank 74 is larger than the capacity of the lower tank 75. Specifically, the capacity of the upper tank 74 is made larger than the capacity of the lower tank 75 to such an extent that an air space compressed during expansion of the refrigerant is formed in the upper tank 74. If such an air space can be secured, even when the outside air temperature rises and the refrigerant expands, it is possible to prevent the occurrence of an accident in which the internal pressure of the radiator is excessively increased and the radiator is damaged.

  As shown in FIG. 12B, a tube connecting cylinder 107 is attached to the refrigerant inlet 80 of the radiator 7, and a tube connecting cylinder 108 is attached to the refrigerant outlet 81. The tube connecting cylinder 107 further includes an inlet side extension pipe part 107 a extending into the lower tank 75 and an outlet side extension pipe part 108 a extending from the refrigerant outlet of the radiator 7 into the lower tank 75. Regardless of the attitude of the radiator 7, the inlet side extension pipe part 107 a and the outlet side extension pipe part 108 a are always arranged so that their terminal openings are located inside the refrigerant. In this way, even when air exists in the lower tank 75 and the liquid level LS is formed in the lower tank 75, the inlet side extension pipe part 107a and the outlet side extension pipe part 108a. Air can be effectively prevented from entering the inside. As a result, it can be suppressed that air is supplied into the electric pump 13 and the performance of the electric pump 13 is deteriorated. In the present embodiment, the termination opening portions of the inlet side extension pipe portion 107a and the outlet side extension pipe portion 108a are terminated at the position of the substantially central portion of the lower tank 75, respectively. Needless to say, the tube connecting cylinders 107 and 108 may be provided in either the upper tank 74 or the lower tank 75.

  The electric pump 13 is disposed so as not to contact the heat radiating portion 71 of the radiator 7. When the electric pump 13 is arranged in such a positional relationship, the possibility that the presence of the electric pump 13 becomes an obstacle to the flow of cooling air is the lowest.

  In order to maximize the function of the radiator 7 for cooling the refrigerant, an object that obstructs the flow of cooling air drawn from the radiator 7 side by the electric fan 5 is placed in front of the heat radiating portion 71 of the radiator 7. Is to be avoided based on the common sense of those skilled in the art. However, in this example, the electric pump 13 is arranged in the impeller non-opposing region 73 that does not face the impeller in the front region of the heat radiating portion 71 of the radiator 7. Although the cooling performance is expected to be slightly lower than when the electric pump is not disposed in front of the heat radiating portion 71, the electric pump 13 can be disposed in the planar shape of the radiator 7. The overall dimension in the planar shape of the component cooling device can be made small. It will be apparent to those skilled in the art that the size of the impeller non-opposing region 73 (FIG. 11) of the heat radiating portion 71 may be appropriately set in order to ensure the required cooling performance.

  As shown in FIGS. 1 and 9, the housing 53 of the electric fan 5 includes a wind tunnel portion 54 and a duct forming wall portion 55. The wind tunnel portion 54 has a suction port 54A facing the impeller facing region 72 of the heat radiating portion 71 of the radiator 7 at one end (rear side) and a discharge port 54B at the other end (front side). The duct forming wall portion 55 is provided continuously with the wind tunnel portion 54 and is configured to guide the cooling air drawn out from the impeller non-opposing region 73 of the heat radiating portion 71 to the suction port 54A.

  The housing 53 includes cover portions 57 and 58 that cover front portions of the upper tank 74 and the lower tank 75 of the radiator 7 at the vertical position of the duct forming wall portion 55. The left and right side wall portions 59 and 60 of the duct forming wall portion 55 are integrally provided with four engagement pieces 61 used for easy attachment of the electric fan 5 to the radiator 7. The radiator 7 is provided with four engaged portions 76 (see FIG. 11) that engage with the four engaging pieces 61 and attach the housing 53 to the radiator 7. In this way, the electric fan 5 can be easily attached to the radiator 7 without using a screw or the like. If the duct forming wall 55 is provided in the housing 53, the cooling air can be drawn out from the impeller non-facing portion 73 of the heat radiating portion 71 that does not directly face the impeller 51, so that the heat radiating portion 71 of the radiator 7 is almost entirely Can be cooled.

  Further, in this embodiment, as shown in FIGS. 3 and 9, an opening 62 is formed in the duct forming wall portion 55 of the housing 53 to expose the heat generating portion including the motor of the electric pump 13. If the electric pump 13 is arranged with the heat generating part including the motor of the electric pump 13 exposed from the opening 62, the heat generated from the electric pump 13 is radiated to the outside of the housing 53 of the electric fan 5, and the radiator 7 can be prevented from being affected.

  As shown in detail in FIG. 3, the fan guard 15 is attached to the outlet 54 </ b> B of the wind tunnel portion 54 of the electric fan 5. The fan guard 15 is attached to the wind tunnel portion 54 via a detachable mounting structure. The guard portion of the fan guard 15 includes four circular rings 15A to 15D, a central circular ring 15E, six connecting bone portions 15F to 15K, and three leg portions 15L to 15N. The four circular rings 15A to 15D are arranged concentrically with the central circular ring 15E, and the six connecting bone portions 15F to 15K extend obliquely radially from the central circular ring 15E toward the circular rings 15A to 15D. ing. Of the six connecting bone portions 15F to 15K, the three connecting bone portions 15K, 15G, and 15I are connected to the three webs 64A to 64C that connect the casing 52A of the motor 52 of the electric fan 5 and the wind tunnel portion 54 to each other. It is arranged along. The feeding line 65 is accommodated in one web 64A of the three webs.

  The three leg portions 15L to 15N are integrally provided on the outermost circular ring 15A at equal intervals in the circumferential direction. In order to easily attach the fan guard 15 to the wind tunnel portion 54, three leg portions 15L provided at equal intervals in the circumferential direction with respect to the outer peripheral portion (circular ring 15A) of the guard portion facing the discharge port 54B. Snap-in type hooks 15P to 15R (see FIG. 1, FIG. 6 to FIG. 8, FIG. 13 and FIG. 14) are provided at the tips of 15 to 15N, respectively. In addition, three engaged portions 65A to 65C (see FIGS. 1, 6 and 7) to which the three hooks 15P to 15R are snap-in coupled are integrally formed on the outer peripheral portion of the wind tunnel portion 54 of the electric fan 5. Provide. The engaged portions 65A to 65C are snap-in coupled to both end portions of the hooks 15P to 15R to enable the hooks to be prevented from being detached and fixed. Further, as shown in FIGS. 6 and 14, a stopper 66 that is provided closer to the housing than the engaged portions 65A to 65C and abuts against the tip portions of the hooks 15P to 15R is integrated with the outer periphery of the wind tunnel portion 54. Is provided. When such a stopper portion 66 is provided, it is possible to prevent the guard from being bent more than necessary due to excessive pressing of the hook and damage to the guard.

  As shown in FIG. 14B, in order to ensure the snap-in coupling, the guard portion of the fan guard 15 is provided with a contact portion 15S that contacts the casing 52A of the electric motor 52. The shape of the contact portion 15S is such that the contact portion 15S is in contact with the casing 52A in a state where the hooks 15P to 15R are engaged with the engaged portions 65A to 65C, and the guard portion approaches the discharge port side 54B. It is determined to be in a bent state. If it does in this way, a hook can be strongly pressed to a to-be-engaged part by the bending of a guard part, and a snap-in coupling | bonding can be ensured.

  As shown in FIGS. 1, 3 and 15, the exterior case 131 of the electric pump 13 exposed from the opening 62 provided in the housing 53 of the electric fan 5 indicates that the electric pump 13 is operating. An operating state display means (132) may be provided. As the operation state display means, it is preferable to provide a light emission display means 132 such as a light emitting diode. When the light emitting display means 132 is provided as the operation state display means, the operation of the electric pump 13 whose operation state cannot be seen from the outside like the electric fan 5 can be confirmed from the outside of the electric fan 5, Confirmation work at the time of repair becomes easy. The light emitting display means 132 may emit light when operating normally, or the light emitting display means 132 may emit light when an abnormality has occurred. In addition, the outer case 131 of the electric pump 13 exposed from the opening 62 has a plurality of heat radiation through holes 133 (FIG. 1, FIG. 1) for releasing heat generated from the heat generating portion of the driving motor disposed inside. (See FIGS. 5, 15, and 16). Providing such a plurality of heat radiating through holes 133 makes it possible to radiate most of the heat generated from the electric pump 13 to the outside of the housing 53 of the electric fan 5. As a result, the influence of heat applied from the electric pump 13 to the radiator 7 can be reduced.

  FIG.15 and FIG.16 is the perspective view which looked at the electric pump 13 from the back side, and the perspective view which looked from the front side. 17 and 18 show a side view and a rear view of the electric pump 13. FIG. 19 is a schematic sectional view taken along line BB in FIG. In FIG. 19, the shape of the inner wall of the wall portion surrounding the impeller storage chamber 137 described later is simply illustrated. FIG. 20 shows a cross-sectional state taken along the line AA in FIG. FIG. 21 is a schematic sectional view taken along the line CC of FIG. As schematically shown in FIG. 19, a driving motor 134 is disposed inside the housing 131 of the electric pump 13. This drive motor 134 is a small motor in which a rotor 134C is disposed at the center of a stator 134B having an excitation winding 134A. A permanent magnet disc 135 having a plurality of driving permanent magnet magnetic poles is attached to the outer peripheral portion of the output shaft 134D of the driving motor 134. The permanent magnet disk 135 is driven by the drive motor 134 to rotate. The interior of the housing 131 is partitioned into a motor storage space 136 and an impeller storage chamber 137 by a partition wall 131A. A plurality of the aforementioned through holes 133 are formed in the peripheral wall portion of the housing 131 that surrounds the electric motor storage space 136. Through these through holes 133, heat generated by the excitation winding 134A of the electric motor 134 is dissipated.

  A pump impeller 138 is rotatably accommodated in the impeller storage chamber 137. The partition wall 131A is provided with a shaft 139 that rotatably supports the impeller 138 so as to protrude toward the impeller storage chamber 137. The impeller 138 includes a cup-shaped member 140 that opens toward the partition wall 131A. A plurality of permanent magnet magnetic poles 141 are fixed to the inner peripheral surface of the peripheral wall portion of the cup-shaped member 140 so as to be opposed to a permanent magnet disk 135 rotated by an electric motor 134 via a partition wall 131A. A plurality of blades 143 arranged radially around the axis of the shaft 139 are integrally provided on the outer surface side of the disk-shaped wall portion of the cup-shaped member 140. With such a configuration, the impeller 138 rotates using the magnetic attractive force generated between the plurality of driving permanent magnet magnetic poles of the permanent magnet disk 135 and the plurality of permanent magnet magnetic poles 141 on the impeller 138 side. With this structure, waterproofing of the electric motor 134 for driving the electric pump can be easily realized.

  The housing 131 includes a liquid inlet 143 and a liquid outlet 144 (FIGS. 19 and 21). Tube connecting cylinders 145 and 146 to which a tube for circulating the refrigerant is connected are integrally provided with the liquid inlet 142 and the liquid outlet 144 (FIG. 21), respectively. A plurality of annular projections for preventing the tube from coming off are integrally formed on the outer peripheral portions of the tube connecting cylinders 145 and 146. The impeller storage chamber 137 is configured to suck the refrigerant from the liquid inlet 142 and discharge it from the liquid outlet 144 when the impeller 138 is immersed in the refrigerant and the impeller 138 rotates. The liquid inlet 142 is formed in the wall 131B facing the plurality of blades 143 among the walls 131B and 131C surrounding the impeller storage chamber 137. The liquid inlet 142 is formed in the wall portion 131 </ b> B so as to be positioned on an extension line of the axis of the shaft 139. As shown in FIG. 21, the liquid outlet 144 is formed in a wall portion (peripheral wall portion) 131 </ b> C located in a direction orthogonal to the axis of the shaft 139.

  In the electric pump 13 of this embodiment, as shown in FIGS. 20 and 21, an annular groove portion 147 and three elongated groove portions 148 are formed in the wall portion 131B where the liquid inlet 142 is formed. The annular groove 147 has a structure that opens toward the impeller 138 so as to completely surround the periphery of the liquid inlet 142. The three elongated grooves 148 are formed outside the annular groove 147 so as not to be continuous with the annular groove 147, extend radially around the axis of the shaft 139 and open toward the impeller 138. ing. The shape and dimensions of the annular groove 147 and the three elongated grooves 148 are such that the dust and bubbles that enter the impeller storage chamber 137 from the liquid inlet 142 are the corners of the blade 143 and the annular groove 147 and the corners of the elongated groove 148. , And is moved radially outward by centrifugal force along the elongated groove and discharged from the liquid outlet 144. Providing such grooves 147 and 148 can effectively prevent the performance of the pump from deteriorating due to dust and bubbles remaining in the impeller storage chamber 137. The elongated groove portions 148 are preferably formed at equal intervals in the circumferential direction as in this example. In this way, the presence of these elongated grooves 148 does not cause uneven rotation of the impeller 138.

  FIG. 22 shows a longitudinal sectional view of another example of the electric pump 13 ′. Parts similar to the structure of the electric pump shown in FIGS. 19 to 21 are denoted by dashes to the reference numerals given in FIGS. 19 to 21 and description thereof is omitted. The electric pump 13 ′ shown in FIG. 22 is an outer rotor type permanent magnet motor in which the rotor 134C ′ of the driving motor 134 ′ rotates outside the stator 134B ′, and the permanent magnet disc 135 ′ is the rotor 134C ′. The permanent magnet magnetic pole 141 'facing the axial direction of the rotating shaft 134D' of the driving motor 134 'and the permanent magnet plate 135' is disposed inside the cup-shaped member 140 '. This is different from the electric pump 13 described above in that the annular groove 147 is not formed in the wall 131B ′ where the liquid inlet 142 ′ is formed. As shown in FIGS. 23 and 24, the wall 131B ′ is formed with three elongated grooves 148 ′ centering on the liquid inlet 142 ′ so as not to be continuous with the liquid inlet 142 ′. A wall surface portion 149 ′ located on the radially outer side of the wall surface surrounding the elongated groove 148 is tapered so as to gradually approach the wall portion 131 B ′. When the taper is formed in this manner, bubbles, dust, and the like that have moved radially outward due to centrifugal force are smoothly discharged from the elongated groove portion without being caught by the edge of the elongated groove portion. Further, compared to the case where the wall surface portion 149 ′ is not tapered, the loss when the impeller 138 ′ is rotated is reduced, and the power consumption can be reduced. Of course, a similar taper may be formed in the elongated groove 148 of the electric pump 13 shown in FIGS.

  25 shows a perspective view of the heat sink 3, and FIGS. 26 and 27 show a plan view and a front view of the heat sink 3, respectively. 28 shows a cross-sectional view taken along line AA in FIG. 27, FIG. 29 shows a cross-sectional view taken along line BB in FIG. 27, and FIG. 30 shows a cross-sectional view taken along line CC in FIG. ing. The heat sink 3 includes a refrigerant flow path therein and includes a base plate 31 and a top plate case 34 including a top plate 32 and a peripheral wall portion 33. The base plate 31 includes an electronic component mounting surface 31a and a heat radiating surface 31b that faces the electronic component mounting surface 31a in the thickness direction and is in direct contact with the refrigerant. The base plate 31 is integrated with a metal having excellent thermal conductivity such as copper or aluminum. Is formed. The top plate case 34 may be formed of a metal having excellent thermal conductivity, such as copper or aluminum, similarly to the base plate 31, but may be formed of a synthetic resin material. The top plate case 34 is provided with a tube connecting cylinder 35 attached to the refrigerant inlet 35a and a tube connecting cylinder 36 attached to the refrigerant outlet 36a.

  The top plate 32 includes a facing surface 32a that faces the heat radiating surface 31b of the base plate 31 with a predetermined gap therebetween. The peripheral wall 33 connects the base plate 31 and the top plate 32 so as to form a chamber 43 (FIG. 30) between the base plate 31 and the top plate 32. The heat sink 3 includes a partition wall portion 37 (FIG. 28 to FIG. 30) that partitions the chamber 43. The partition wall portion 37 is coupled or closely adhered to one (33a) of the pair of peripheral wall constituting portions 33a and 33b opposed to the peripheral wall portion 33 and extends toward the other (33b). In order to obtain a bond, for example, an adhesion or welding technique may be used. For the close contact, a pressing technique or a tight fitting technique may be used. Due to the presence of the partition wall portion 37, first and second divided chambers 38 and 39 are formed on both sides of the partition wall portion 37 in the chamber 43, and the partition wall portion 37 and the other of the pair of peripheral wall components (33 b ), A communication passage 40 that communicates the first and second divided chambers 38 and 39 is formed. The refrigerant inlet 35 a of the heat sink 3 is provided so as to communicate with the first chamber partial region 38 a located on the opposite side of the communication passage 40 of the first divided chamber 38. The refrigerant outlet 36 a of the heat sink 3 is provided so as to communicate with the second chamber partial region 39 a located on the opposite side of the communication path 40 of the second divided chamber 39. By doing so, the refrigerant inlet 35a and the refrigerant outlet 36a of the heat sink 3 are arranged at positions close to each other, and the connection of the pipe to the heat sink 3 is facilitated, and the presence of the pipe fixes the heat sink 3. Less likely to become an obstacle. In each of the first and second divided chambers 38 and 39, a plurality of plate-like radiating fins 41 provided so as to be able to transfer heat to at least the base plate 31 are arranged so as not to prevent the refrigerant from flowing. . The refrigerant that has entered the first divided chamber 38 from the refrigerant inlet 35 comes into contact with the plurality of radiating fins 41 in the first divided chamber 38, and then the second chamber partial region 38b of the first divided chamber 38, The fourth chamber partial region 39a enters the third chamber partial region 39b of the second divided chamber 39 through the communication passage 40 and comes into contact with the plurality of plate-like heat radiation fins 41 in the second divided chamber 39. And is discharged from the refrigerant outlet 36a. With such a structure, the cooling performance is improved without increasing the shape of the heat sink. The reason is that the ratio of the width dimension of the first divided chamber 38 and the second divided chamber 39 to the diameter dimension of the refrigerant inlet 35a and the refrigerant outlet 36a is not so large, so This is because there is no large difference in the flow velocity and flow rate of the refrigerant flowing in the gap between the radiating fins 41, and heat transfer from each radiating fin 41 to the refrigerant is performed without delay. As a result, the cooling performance can be improved without increasing the shape and size of the heat sink 3.

  In this example, the plurality of radiating fins used in the present invention are configured by a plurality of plate-shaped radiating fins 41 extending alongside the partition wall portion 37. In this case, a gap through which the refrigerant flows is formed between two adjacent plate-like heat radiation fins 41. The thickness of the plate-like heat radiation fin 41 and the width dimension of the gap may be determined so that necessary cooling performance can be obtained. The base plate 31, the partition wall portion 37, and the plurality of plate-like heat radiation fins 41 can be integrally formed. Then, the partition wall portion 37 and the tips of the plurality of plate-like heat radiation fins 41 are coupled or brought into close contact with the top plate 32. In order to obtain a bond, for example, an adhesion or welding technique may be used. For the close contact, a pressing technique or a tight fitting technique may be used. When such a configuration is adopted, the refrigerant does not flow between the upper end of the radiating fin 41 and the top plate 31, and the circulation of the refrigerant is limited only to the gap between the radiating fins. As a result, it is possible to effectively prevent the amount of heat transfer from the heat radiating fins to the refrigerant, and to improve the cooling performance.

  Note that the refrigerant inlet 35a and the refrigerant outlet 36a of the heat sink 3 are formed in the top plate 32 in this example. This makes it easy to connect the pipe to the heat sink 3 and the presence of the pipe is less likely to become an obstacle when the heat sink 3 is fixed.

  In this example, the plurality of plate-like radiating fins 41 includes a first chamber partial region 38a and a second chamber partial region 38b, and a third chamber partial region 39b and a fourth chamber sandwiching the communication passage 40 therebetween. It arrange | positions in the position except the partial area | region 39a. If the occupied volume of the heat radiating fins in the chamber 43 is increased more than necessary, the flow rate of the refrigerant decreases, and the cooling performance deteriorates.

  Further, the inner wall surface portion 42 of the peripheral wall portion 33 surrounding the four corners of the chamber 35 is configured by a curved surface that does not form a corner portion. If it does in this way, the flow-path resistance in the corner | angular part in the chamber 35 can be made small, and the fall of an unnecessary flow velocity can be suppressed.

  The tube connecting cylinders 35 and 36 are connected to the refrigerant inlet 35a and the refrigerant outlet 36a formed in the top plate 32 by soldering or brazing. Hereinafter, the tube connecting cylinder 36 shown in FIG. 28 will be described as an example. An annular space 36A for receiving solder or brazed molten metal leaking from the refrigerant outlet 36a to the surface side of the top plate 32 is provided on the outer peripheral portion of the tube connecting cylinder 36 from the top plate 32. A flange 36B is provided integrally. The flange portion 36B is an annular plate portion 36D that is integrally fixed to the outer peripheral portion of the cylindrical main body 36C and extends in the radial direction, and a cylindrical portion 36E that extends from the end of the plate portion 36D along the cylindrical main body 36C. Consists of

  When such a flange 36B is provided on the tube connecting cylinder 36, soldering or brazing between the back surface of the top plate 32 and the outer peripheral surface of the base of the cylindrical main body 36C of the tube connecting cylinder 36. Therefore, it is possible to prevent the molten metal from leaking in a form visible from the outside to the surface side of the top plate 32. The top plate 32 and the base plate 31 are coupled to each other by solder or brazing material filled in a step portion 31A formed on the outer peripheral portion of the base plate 31. If the outer surface of the heat sink is subjected to treatment such as plating, painting or shot blasting, the appearance of the heat sink can be made more beautiful.

  FIG. 31 shows that the tube 90 is fitted to the end of the tube connecting cylinder used in the heat sink 3, the radiator 7 and the electric pump 13 (representing one tube connecting cylinder 36 of the heat sink 3 as a representative example). An enlarged sectional view of the combined state is shown. On the outer peripheral portion of the end of the tube connecting cylinder 36, a tapered surface 36F having a diameter that increases from the distal end toward the base, and an edge that bites into the inner wall of the tube is formed between the tapered surface 36F. Thus, three edge forming protrusions 36H having an edge forming surface 36G extending from the top of the tapered surface 36F toward the tubular main body 36C of the tube connecting tube 36 are integrally provided. When one or more edge forming protrusions 36H are provided, the edge of the edge forming protrusion 36H can be bitten into the inner wall of the tube 90 in the process of fitting the tube 90 to the tube connecting cylinder 36. Thus, the tube 90 can be firmly prevented from coming off. In addition, the edge of the edge forming protrusion provided on the tube connecting tube bites into the inner wall of the tube, so there is no gap between the two, greatly reducing liquid leakage or liquid evaporation at the connecting portion. be able to.

  The tube is preferably made of a material that is excellent in heat resistance, chemical resistance, and weather resistance and does not have much flexibility and stretchability. As the currently preferred tube 90, a plastic tube is preferable, and in the present embodiment, a tube formed of a fluororesin is used. As this fluororesin, it is preferable to use a fluororesin having low water permeability. If it does in this way, it can control that a refrigerant permeate | transmits the outer wall part of the tube 90, and a refrigerant | coolant reduces. A spiral groove 91 or a bellows-shaped groove 91 extending in the longitudinal direction of the tube 90 is formed on the outer peripheral portion of the main portion of the tube 90. If such a groove 91 is formed, even when the tube 90 is not flexible or stretchable, the bending work when the heat sink is attached becomes easy.

  FIGS. 32A to 32F show the left side of the electronic component cooling apparatus in which a gasket 14 made of an elastic material such as sponge or rubber is attached to the outer peripheral edge portion of the surface of the radiator 7 that is not opposed to the electric fan 5. A side view, a front view, a bottom view, a plan view, a right side view, and a rear view are shown. The gasket 14 includes four linear gasket members 14a to 14d. On both side surfaces of the radiator 7, gasket holders 16 that respectively support the gasket members 14 a and 14 b are attached. 33 (A) and 33 (B) show a front view and a right side view of the gasket holder 16, and FIG. 33 (C) shows a deformation of the gasket member 14a when the gasket holder 16 is not used and when the gasket holder 16 is used. It is sectional drawing which shows an aspect. The gasket holder 16 supports the gasket members 14a and 14b constituting a part of the gasket 14 in a state separated from the heat radiating portion 71, and the gasket member is attached when the gasket members 14a and 14b are pressed toward the attached portion. The deformation of the gasket member is regulated so as to be in close contact with the portion in a stable state. The gasket holder 16 is integrally provided with a main body 162 having a support surface 161 that supports the gasket member 14a or 14b, and two mounting hooks 163 provided on the main body 162. The mounting hook 163 is locked to the side of the heat radiating portion 71 of the radiator 7. The main body 162 is provided with extended portions 164 at both ends thereof. The extension 164 extends along the ends of the gasket members 14c and 14d attached to the outer surfaces of the upper tank 74 and the lower tank 75, and restricts deformation of the gasket members 14c and 14d.

  In the present embodiment, the gasket support member is constituted by the two gasket holders 16. As shown in FIG. 33 (C), when the gasket support member is used, the gasket 14 can be constantly deformed in a stable manner without being attached to a position that affects the cooling performance. Can be prevented. Since the gasket holder 16 is detachably attached to the radiator 7, there is no need to mount the gasket holder 16 when it is not necessary to use a gasket.

  According to the present invention, it is possible not only to cool an electronic component having a large calorific value to a necessary and sufficient level by so-called water cooling (liquid cooling), but also to arrange an electric pump in the planar shape dimension of the radiator. Therefore, there is an advantage that the overall size of the electronic component cooling device can be reduced without greatly reducing the cooling performance.

DESCRIPTION OF SYMBOLS 1 Electronic component cooling device 3 Heat sink 5 Electric fan 7 Radiator 13 Electric pump 31 Base plate 32 Top plate 35 Tube connection cylinder (refrigerant inlet)
36 Tube connection cylinder (refrigerant outlet)
31a Electronic component mounting surface 31b Heat dissipation surface

Claims (20)

A heat sink comprising an electronic component mounting surface on which an electronic component to be cooled is mounted, a refrigerant inlet and a refrigerant outlet, and a refrigerant channel through which a liquid as a refrigerant for forcibly cooling the electronic component mounting surface flows When,
A radiator having a refrigerant inlet and a refrigerant outlet and through which the refrigerant flows, and a radiator that cools the refrigerant by cooling the liquid passage by air cooling;
An electric fan mounted on a radiator of the radiator and supplying cooling air to the radiator;
A first refrigerant passage connecting the refrigerant outlet of the heat sink and the refrigerant inlet of the radiator;
A second refrigerant passage connecting the refrigerant outlet of the radiator and the refrigerant inlet of the heat sink;
An electric pump that is disposed in the first refrigerant passage or the second refrigerant passage and gives kinetic energy to the refrigerant;
The heat sink is
A base plate provided with a heat radiating surface that is in direct contact with the refrigerant facing the electronic component mounting surface and the thickness direction of the electronic component mounting surface;
A top plate having a facing surface facing the heat radiating surface of the base plate with a predetermined gap therebetween;
A peripheral wall portion that connects the base plate and the top plate so as to form a chamber between the base plate and the top plate, and one of a pair of peripheral wall constituent portions facing the peripheral wall portion that are coupled or closely adhered to each other A partition wall portion extending toward the base plate and bonded or closely adhered to both the base plate and the top plate,
In the chamber, first and second divided chambers are formed on both sides of the partition wall, and the first and second partitions are formed between the partition wall and the other of the pair of peripheral wall components. A communication path communicating with the chamber is formed,
The refrigerant inlet of the heat sink communicates with a first chamber partial region located on the opposite side of the communication path of the first divided chamber, and the refrigerant outlet of the heat sink is connected to the second divided chamber. In communication with the second chamber partial region located on the opposite side of the communication passage of
In the first and second divided chambers, a plurality of radiating fins provided so as to be able to transfer heat to at least the base plate are arranged so as not to prevent the refrigerant from flowing. Electronic component cooling device.   The plurality of radiating fins include a plurality of plate-shaped radiating fins extending alongside the partition wall, and a gap through which the refrigerant flows is formed between two adjacent plate-shaped radiating fins. Item 2. The electronic component cooling apparatus according to Item 1. The base plate, the partition wall, and the plurality of plate-shaped heat radiation fins are integrally formed,
3. The electronic component according to claim 2, wherein the top plate and the peripheral wall portion are integrally formed, and the partition wall portion and the tips of the plurality of plate-shaped heat radiation fins are coupled or in close contact with the top plate. Cooling system.   The electronic component cooling device according to claim 1, wherein the refrigerant inlet and the refrigerant outlet of the heat sink are formed in the top plate.   The plurality of plate-like radiating fins excludes the first chamber partial region and the second chamber partial region, and the third chamber partial region and the fourth chamber partial region sandwiching the communication path therebetween. The electronic component cooling device according to claim 2, wherein the electronic component cooling device is disposed at a position.   The electronic component cooling device according to claim 1, wherein a portion of the inner wall surface of the peripheral wall portion surrounding the four corners of the chamber is configured by a curved surface that does not form a corner portion. A tube connecting cylinder is connected to the refrigerant inlet and the refrigerant outlet formed in the top plate by soldering or brazing,
A flange portion having an annular space for receiving molten metal leaking from the refrigerant inlet or the refrigerant outlet to the surface side of the top plate is integrally provided on the outer peripheral portion on the base side of the tube connecting cylinder. The electronic component cooling device according to claim 4. The electric pump is
An impeller comprising a plurality of radially extending blades and rotating about an axis;
An impeller housing that includes a liquid inlet and a liquid outlet, and is configured such that when the impeller is immersed in the refrigerant and the impeller rotates, the refrigerant is sucked from the liquid inlet and discharged from the liquid outlet. A housing with a chamber inside,
The liquid inlet is formed so as to be positioned on an extension line of the axis line on a wall portion facing the plurality of blades among a plurality of wall portions surrounding the impeller storage chamber,
The liquid outlet is formed in a wall portion located in a direction orthogonal to the axis among the plurality of wall portions,
The wall portion in which the liquid inlet is formed includes an annular groove portion that opens toward the impeller so as to completely surround the periphery of the liquid inlet, and the annular groove portion outside the annular groove portion. A plurality of elongated grooves that are formed so as not to be continuous and extend radially about the axis and open toward the impeller side are formed,
The shape and dimensions of the annular groove and the plurality of elongated grooves are such that dust and bubbles that enter the impeller storage chamber from the liquid inlet are caused by corners of the plurality of blades, the annular groove, and the elongated grooves. It is determined so that it may be crushed between the corners of the liquid crystal and moved radially outward by centrifugal force along the elongated groove and discharged from the liquid outlet. Electronic component cooling system. The electric pump is
An impeller comprising a plurality of radially extending blades and rotating about an axis;
An impeller housing that includes a liquid inlet and a liquid outlet, and is configured such that when the impeller is immersed in the refrigerant and the impeller rotates, the refrigerant is sucked from the liquid inlet and discharged from the liquid outlet. A housing with a chamber inside,
The liquid inlet is formed so as to be positioned on an extension line of the axis line on a wall portion facing the plurality of blades among a plurality of wall portions surrounding the impeller storage chamber,
The liquid outlet is formed in a wall portion located in a direction orthogonal to the axis among the plurality of wall portions,
A plurality of elongated grooves that are formed so as not to be continuous with the liquid inlet and extend radially about the axis and open only toward the impeller side in the wall portion where the liquid inlet is formed. Is formed,
The shape and size of the plurality of elongated grooves are such that dust and bubbles that enter the impeller storage chamber from the liquid inlet are crushed between the plurality of blades and corners of the edges of the elongated grooves. The electronic component cooling device according to claim 1, wherein the electronic component cooling device is defined so as to move radially outward along the elongated groove portion by a centrifugal force and to be discharged from the liquid outlet. The radiator has a structure in which the heat radiating portion is disposed between an upper tank and a lower tank,
When the direction from the electric fan toward the radiator is the thickness direction of the radiator, the dimension of the upper tank and the lower tank in the thickness direction is made larger than the dimension of the heat dissipation portion in the thickness direction. The electronic component cooling apparatus according to claim 1.   The electronic component cooling device according to claim 1, wherein mounting brackets that are used when the upper tank and the lower tank are respectively attached to the mounted portions are integrally provided on the outer wall portions of the upper tank and the lower tank.   The electronic component cooling device according to claim 1, wherein the refrigerant is sealed in a system including a radiator in a pressure state lower than atmospheric pressure. Tube connecting cylinders extending outward are provided at the fluid inlet and the fluid outlet of the radiator, the refrigerant inlet and the refrigerant outlet of the heat sink, and the liquid inlet and the liquid outlet of the pump, respectively.
The both ends of the flexible tube are respectively fitted to the outer peripheral portions of the two corresponding tube connecting cylinders,
The tapered surface is formed so that an outer periphery of the tube connecting cylinder has a tapered surface whose diameter increases from the distal end toward the base, and an edge that bites into the inner wall of the tube between the tapered surface. The electronic component cooling device according to claim 1, further comprising one or more edge forming protrusions including an edge forming surface extending from the top of the tube connecting tube toward the tube connecting cylinder. A heat sink comprising an electronic component mounting surface on which an electronic component to be cooled is mounted, a refrigerant inlet and a refrigerant outlet, and a refrigerant channel through which a liquid as a refrigerant for forcibly cooling the electronic component mounting surface flows Because
A base plate provided with a heat radiating surface that is in direct contact with the refrigerant facing the electronic component mounting surface and the thickness direction of the electronic component mounting surface;
A top plate having a facing surface facing the heat radiating surface of the base plate with a predetermined gap therebetween;
A peripheral wall portion that connects the base plate and the top plate so as to form a chamber between the base plate and the top plate, and one of a pair of peripheral wall constituent portions facing the peripheral wall portion that are coupled or closely adhered to each other A partition wall portion extending toward the base plate and bonded or closely adhered to both the base plate and the top plate,
In the chamber, first and second divided chambers are formed on both sides of the partition wall, and the first and second partitions are formed between the partition wall and the other of the pair of peripheral wall components. A communication path communicating with the chamber is formed,
The refrigerant inlet of the heat sink communicates with a first chamber partial region located on the opposite side of the communication path of the first divided chamber, and the refrigerant outlet of the heat sink is connected to the second divided chamber. In communication with the second chamber partial region located on the opposite side of the communication passage of
In the first and second divided chambers, a plurality of radiating fins provided so as to be able to transfer heat to at least the base plate are arranged so as not to prevent the refrigerant from flowing. Heat sink. The refrigerant inlet and the refrigerant outlet of the heat sink are formed in the top plate,
A tube connecting cylinder is connected to the refrigerant inlet and the refrigerant outlet formed in the top plate by soldering or brazing,
A flange portion having an annular space for receiving molten metal leaking from the refrigerant inlet and the refrigerant outlet to the surface side of the top plate is integrally provided on the outer peripheral portion on the base side of the tube connecting cylinder. The heat sink according to claim 14. An impeller comprising a plurality of radially extending blades and rotating about an axis;
An impeller storage chamber having a liquid inlet and a liquid outlet, wherein the impeller is immersed in the liquid and configured to suck the liquid from the liquid inlet and discharge the liquid from the liquid outlet when the impeller rotates. And a housing with an inside,
The liquid inlet is formed so as to be positioned on an extension line of the axis on a wall portion facing the plurality of blades among a plurality of wall portions of the housing surrounding the impeller storage chamber,
The liquid outlet is formed in a wall portion located in a direction orthogonal to the axis among the plurality of wall portions,
The wall portion in which the liquid inlet is formed includes an annular groove portion that opens toward the impeller so as to completely surround the periphery of the liquid inlet, and the annular groove portion outside the annular groove portion. A plurality of elongated grooves that are formed so as not to be continuous and extend radially about the axis and open toward the impeller side are formed,
The shape and dimensions of the annular groove and the plurality of elongated grooves are such that dust and bubbles that enter the impeller storage chamber from the liquid inlet are caused by corners of the plurality of blades, the annular groove, and the elongated grooves. The electric pump is characterized in that it is crushed at the corners of the nozzle, moved radially outward by centrifugal force, and discharged from the liquid outlet. An impeller comprising a plurality of radially extending blades and rotating about an axis;
An impeller storage chamber having a liquid inlet and a liquid outlet, wherein the impeller is immersed in the liquid and configured to suck the liquid from the liquid inlet and discharge the liquid from the liquid outlet when the impeller rotates. And a housing with an inside,
The liquid inlet is formed so as to be positioned on an extension line of the axis on a wall portion facing the plurality of blades among a plurality of wall portions of the housing surrounding the impeller storage chamber,
The liquid outlet is formed in a wall portion located in a direction orthogonal to the axis among the plurality of wall portions,
A plurality of elongated grooves that are formed so as not to be continuous with the liquid inlet and extend radially about the axis and open only toward the impeller side in the wall portion where the liquid inlet is formed. And are formed,
The shape and dimension of the plurality of elongated grooves are such that dust and bubbles that enter the impeller storage chamber from the liquid inlet are crushed at the corners of the blades and the elongated grooves, along the elongated grooves. The electric pump is characterized in that it is determined to move radially outward by centrifugal force and to be discharged from the liquid outlet.   18. A wall surface portion located radially outside of the wall surface surrounding the elongated groove is tapered so as to gradually approach toward the wall portion facing the plurality of blades. The electric pump as described in. A heat sink comprising an electronic component mounting surface on which an electronic component to be cooled is mounted, a refrigerant inlet and a refrigerant outlet, and a refrigerant channel through which a liquid as a refrigerant for forcibly cooling the electronic component mounting surface flows When,
A radiator including a refrigerant inlet and a refrigerant outlet and a liquid channel through which the refrigerant flows, and the liquid channel is cooled by air cooling to cool the refrigerant;
An electric fan mounted on a radiator of the radiator and generating air cooling air by rotation of an impeller provided with a plurality of blades to cool the radiator of the radiator;
The refrigerant flowing out from the refrigerant outlet of the radiator is supplied to the refrigerant inlet of the heat sink, and the moving energy of supplying the refrigerant flowing out of the refrigerant outlet of the heat sink to the refrigerant inlet of the radiator is given to the refrigerant. With an electric pump,
Electronic component cooling in which the radiator is fixed to the mounted portion via a gasket made of an elastic material between an outer peripheral edge portion of a surface located on the side of the radiator not facing the electric fan and the mounted portion. A device,
The radiator is supported so that the gasket is separated from the heat radiating portion, and the gasket is in close contact with the mounted portion in a stable state when the gasket is pressed toward the mounted portion. An electronic component cooling apparatus comprising a gasket support member for restricting deformation of the gasket.   The electronic component cooling device according to claim 19, wherein the gasket support member is detachably attached to the radiator.

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