Dual Tower CPU Cooler Having Support Bracket for Suppressing Tilting of Heat Sink

Abstract

A dual-tower type CPU cooler having a support member that suppresses tilting of a heat sink according to the present invention is characterized by comprising: a base plate that absorbs heat by contacting a CPU; a plurality of heat pipes coupled to the base plate to receive heat; a first heat sink and a second heat sink connected to the plurality of heat pipes to release heat; and a support member that connects the lower ends of the first and second heat sinks to each other to suppress tilting of the first and second heat sinks. According to the dual tower type CPU cooler equipped with a support that suppresses tilting of the heat sink according to the present invention, by physically restraining the lower portions of the first and second heat sinks with the support, tilting caused by self-weight, external shock, and vibration is fundamentally suppressed, and a stable thermal contact state between the base plate and the upper surface of the CPU is maintained for a long period of time.

Description

Technology Field

[0001] The present invention relates to a dual-tower type CPU cooler equipped with a support that suppresses tilting of a heat sink, and more specifically, to a CPU cooler in which the lower portions of the first and second heat sinks formed in a dual-tower type are interconnected by a support to suppress tilting of the heat sinks caused by self-weight and external impact, thereby enabling a stable thermal contact state between the base plate and the CPU to be maintained for a long period of time. Background Technology

[0002] The CPU (Central Processing Unit) is the core computational component of a computer system and generates significant heat during operation. If this generated heat is not effectively dissipated, throttling occurs, which forcibly lowers the CPU's operating frequency, leading to performance degradation and, in severe cases, permanent damage to the CPU.

[0003] Accordingly, cooling technology to ensure stable CPU operation is treated as a very important element in computer system design.

[0004] CPU cooling methods are broadly classified into water cooling and air cooling.

[0005] Although water cooling offers excellent cooling performance, its complex structure and risk of leakage make it primarily used in high-performance workstations or server environments rather than for general consumer systems.

[0006] On the other hand, air cooling is the most widely adopted cooling method in general consumer desktop PCs due to its simple structure, ease of installation, and simple maintenance. Air-cooled CPU coolers typically consist of a base plate that makes direct contact with the CPU, heat pipes that transfer heat, a heat sink that releases the transferred heat into the air, and a fan that generates forced convection.

[0007] Recently, as the amount of heat generated by CPUs continues to increase, the demand for cooling performance is also rising. In response to this, dual tower type CPU coolers that separate the heat sink into two and place them side by side have been developed and are becoming widely available.

[0008] Dual-tower CPU coolers have the advantage of significantly expanding the heat dissipation area compared to single-tower types, and can supply forced convection to both heat sinks simultaneously by mounting a fan in the gap between the two heat sinks, resulting in excellent cooling performance.

[0009] However, dual-tower CPU coolers inevitably require an increased height of the heat sink to secure sufficient heat dissipation area, and the overall weight of the cooler is considerable due to the structure combining two heat sinks, multiple heat pipes, and fans.

[0010] When such a tall and heavy structure is mounted on the CPU socket via a base plate, the heat sink shows a strong tendency to tilt sideways due to its own weight and external impacts.

[0011] In particular, in a structure where two heat sinks are supported solely by heat pipes, repetitive stress is concentrated at the joint between the heat pipes and the heat sinks, which can lead to damage to the joint and a decrease in heat transfer performance. Additionally, if tilting of the heat sinks accumulates, the thermal contact between the base plate and the top surface of the CPU becomes uneven, leading to localized overheating. Furthermore, if external impact is applied during movement or transportation without a fan installed, the heat sinks may shift sideways or deform, resulting in reduced structural reliability of the cooler.

[0012] Conventionally, structures that supported heat sinks relying solely on the bonding force of heat pipes without separate means to solve these problems were common; consequently, there were limitations in fundamentally suppressing the tilting of the heat sink and maintaining a stable thermal contact state in long-term usage environments.

[0013] Therefore, there is a need for the development of technology for a structural solution that can fundamentally suppress tilting caused by the self-weight and external impact of the heat sink in a dual-tower type CPU cooler and maintain a stable thermal contact state between the base plate and the top surface of the CPU for a long period of time. Prior art literature

[0014] Korean Registered Patent No. 10-0891994 The problem to be solved

[0015] The present invention was devised to overcome the problems of the above technology, and its main purpose is to provide a CPU cooler that supports the lower portions of the first and second heat sinks in a dual-tower type CPU cooler to suppress tilting of the heat sinks caused by self-weight and external impact, and maintains a stable thermal contact state between the base plate and the upper surface of the CPU for a long period of time.

[0016] Another objective of the present invention is to ensure structural reliability by forming the support into a multi-stage bending structure consisting of first and second fastening bars, a pair of bending extensions, and a connecting bar, thereby simultaneously restraining the left-right tilting, back-and-forth shaking, and inner-outer spreading of the first and second heat sinks.

[0017] Another objective of the present invention is to prevent fatigue failure of the fastening part and maintain a stable fastening state for a long period of time by forming the first and second fastening holes as elongated holes and adopting a fastening structure that combines an annular bushing and an elastic washer, thereby allowing dimensional changes due to thermal expansion and tilting behavior of the heat sink while absorbing fan driving vibrations. means of solving the problem

[0018] To achieve the above objective, a dual-tower type CPU cooler according to the present invention, equipped with a support that suppresses tilting of a heat sink, is characterized by comprising: a base plate that absorbs heat by contacting a CPU; a plurality of heat pipes coupled to the base plate to receive heat; a first heat sink and a second heat sink connected to the plurality of heat pipes to release heat; and a support that connects the lower ends of the first and second heat sinks to each other to suppress tilting of the first and second heat sinks.

[0019] In addition, the support member is characterized by comprising a first fastening bar having a first fastening hole formed through it to be fastened via a fastener to be fastened to the lower end of the first heat sink, a second fastening bar having a second fastening hole formed through it to be fastened via a fastener to be fastened to the lower end of the second heat sink, a pair of bent extensions that are each bent downward from the ends of the first and second fastening bars, and a connecting bar that connects the lower ends of the pair of bent extensions to each other, and is arranged in a plurality at regular intervals along the front-rear direction of the first and second heat sinks.

[0020] In addition, the first and second fastening holes are each formed as long holes with a long axis formed along the extension direction of the first and second fastening bars, and an annular bushing made of an elastic material is fitted onto the outer surface of the fastener and adheres to the inner surface in the short axis direction of the long hole, and an elastic washer having an inner diameter smaller than the outer diameter of the fastener head and an outer diameter larger than the width of the long axis of the long hole is interposed between the head of the fastener and the surface of the first and second fastening bars, so that the annular bushing and the fastener move relative to each other in the long axis direction of the long hole and axial vibration absorption by the elastic washer is simultaneously achieved. Effects of the invention

[0021] According to the dual-tower type CPU cooler having a support that suppresses tilting of a heat sink according to the present invention,

[0022] 1) By physically restraining the lower portions of the first and second heat sinks with supports, it has the advantage of fundamentally suppressing tilting caused by self-weight, external shock, and vibration, and maintaining a stable thermal contact state between the base plate and the upper surface of the CPU for a long period of time,

[0023] 2) By means of a fastening structure composed of a combination of elongated holes, annular bushings, and elastic washers, dimensional changes due to thermal expansion and tilting behavior are naturally allowed, while axial vibrations caused by fan driving are absorbed, thereby preventing fatigue failure of the fastening part and maintaining a stable fastening state for a long period, and

[0024] 3) By additionally providing a reinforcing plate and an opening in the support, the structural rigidity of the support is increased, while simultaneously minimizing vibration amplification, blockage of air passages, and weight increase, thereby having the effect of simultaneously improving cooling performance and durability. Brief explanation of the drawing

[0025] FIG. 1 is a perspective view showing the overall appearance of the CPU cooler of the present invention. Figure 2 is a magnified view of the area around the support in Figure 1. FIG. 3 is a perspective view illustrating the detailed structure of the support of the present invention. FIG. 4 is a longitudinal section view in the short axis direction around the first and second fastening holes of the present invention. Fig. 5 is a cross-sectional view of AA of Fig. 4. FIG. 6 illustrates the structure of the guide groove and guide projection of the present invention, where the left side is a plan view of the surface around the elongated hole of the fastening bar and the right side is a plan view of the bottom surface of the elastic washer. FIG. 7 is a perspective view illustrating a first modified embodiment of the support of the present invention. FIG. 8 is a perspective view showing the first and second heat sinks mounted on the support of FIG. 7. FIG. 9 is a perspective view illustrating a modified embodiment of the support of the present invention. Specific details for implementing the invention

[0026] Preferred embodiments of the present invention will be described in detail below with reference to the attached drawings. The attached drawings are not drawn to scale, and the same reference numerals in each drawing refer to the same components.

[0027] The CPU cooler of the present invention has the main purpose of suppressing tilting by connecting the lower ends of the first and second heat sinks to each other with supports in order to solve the problem of the heat sink tilting relative to the base plate due to the height and self-weight of the heat sink in a CPU cooler employing a dual tower type heat sink.

[0028] FIG. 1 is a perspective view showing the overall appearance of the CPU cooler of the present invention, and FIG. 2 is a partial enlarged view of the area around the support in FIG. 1.

[0029] As can be seen from FIG. 1, the CPU cooler of the present invention is based on including a base plate (10), a heat pipe (20), a first heat sink (30) and a second heat sink (40) and a support (100).

[0030] The base plate (10) is a plate-shaped member that directly contacts the upper surface of the CPU to absorb heat generated from the CPU and is mounted at a position corresponding to the CPU socket.

[0031] The base plate (10) is made of copper (Cu) or aluminum (Al) material with excellent thermal conductivity, and in the case of copper material, the thermal conductivity reaches about 400 W / m·K, so it can quickly absorb heat generated from the CPU.

[0032] The lower surface of the base plate (10) is machined to a mirror-like level to minimize thermal contact resistance with the upper surface of the CPU, and a thermal compound, which is a thermal interface material (TIM), is applied between the base plate (10) and the upper surface of the CPU to prevent the formation of an air layer due to fine surface irregularities.

[0033] A plurality of grooves or slots are formed on the upper surface of the base plate (10) into which a heat pipe (20) is inserted and connected, thereby securing a contact area with the heat pipe (20) and increasing heat transfer efficiency.

[0034] The outer shape of the base plate (10) is generally formed as a rectangle corresponding to the specifications of the CPU socket, and a fastening hole (not shown) for fixing to the motherboard is formed at the corner.

[0035] The thickness of the base plate (10) can be formed in a range of 3mm to 10mm considering the heat capacity and heat diffusion performance, but if the thickness is too thin, heat diffusion becomes uneven and if it is too thick, the weight of the entire cooler increases, so it is appropriately designed within this range.

[0036] The heat pipe (20) is a heat transport member that is coupled to the base plate (10) and transfers the heat absorbed by the base plate (10) to the first and second heat sinks (30, 40).

[0037] The heat pipe (20) can be configured with a working fluid enclosed inside, in which case the working fluid repeats a cycle of evaporating at a high temperature and condensing at a low temperature to transfer heat, thereby exhibiting significantly higher heat transfer performance compared to a simple metal conductor.

[0038] Meanwhile, the heat pipe (20) may be configured in the form of a solid metal rod that does not contain an operating fluid inside, and in this case, heat transfer from the base plate (10) to the first and second heat sinks (30, 40) is achieved by heat conduction of a high thermal conductivity material such as copper.

[0039] That is, the internal structure of the heat pipe (20) in the present invention is not particularly limited, and any one of the above-described forms may be selectively applied depending on the design conditions and required performance.

[0040] The external shape of the heat pipe (20) is formed as a cylindrical shape with a circular cross-section, but at the joint portion with the base plate (10), it is formed flat by compression processing and closely joined to the groove of the base plate (10) to maximize the thermal contact area.

[0041] The material of the heat pipe (20) is generally formed from copper (Cu), which has excellent thermal conductivity and processability, and the outer diameter can be formed in the range of 5 mm to 10 mm.

[0042] A plurality of heat pipes (20) are provided, each having one end inserted into a groove of a base plate (10) and fixedly connected by soldering or sintering, and the other end passing through a first heat sink (30) and a second heat sink (40) and connected to each heat dissipation plate.

[0043] That is, the heat pipes (20) are evenly distributed on the base plate (10) in correspondence with the location of the CPU heat source, thereby uniformly absorbing heat from the heat source and distributing it evenly throughout the first and second heat sinks (30, 40).

[0044] The first heat sink (30) and the second heat sink (40) are heat dissipation members that receive heat from the heat pipe (20) and release it to the outside air, and are spaced apart from each other and arranged side by side.

[0045] The first heat sink (30) and the second heat sink (40) are each formed in a tower shape by stacking a plurality of heat dissipation plates in a vertical direction.

[0046] At this time, the heat dissipation plates are formed from thin sheets of metal material with excellent thermal conductivity, such as aluminum (Al), copper (Cu), or alloys thereof, and a predetermined gap is maintained between each heat dissipation plate to allow air to circulate.

[0047] As an example, the thickness of the heat dissipation plate may be in the range of 0.3 mm to 0.8 mm, and the gap between adjacent heat dissipation plates may be in the range of 1.5 mm to 3.0 mm.

[0048] Each heat dissipation plate has a plurality of through holes formed therein through which a heat pipe (20) passes and is joined, and the outer surface of the heat pipe (20) and the inner surface of the through holes are closely joined by soldering or compression so that heat transfer from the heat pipe (20) to each heat dissipation plate is smoothly achieved.

[0049] The first heat sink (30) and the second heat sink (40) can be arranged in various forms such as front and back, left and right, or diagonal directions, but it is preferable that they be arranged side by side in a spaced-apart state to minimize the width dimension of the entire cooler and simplify the connection structure with the heat pipe (20).

[0050] Furthermore, by arranging the first and second heat sinks (30, 40) side by side, the gap between them can be naturally utilized as a fan mounting portion (50), and when a fan (not shown) is mounted, external air is forced to flow between the heat dissipation plates of the first and second heat sinks (30, 40) when the fan is operated, thereby further improving heat dissipation performance.

[0051] In other words, the fan mounting portion (50) can provide a function to improve heat dissipation performance by forced convection by utilizing the space between the first and second heat sinks (30, 40) to stably support the fan without a separate mounting structure.

[0052] As such, the first and second heat sinks (30, 40) are formed as a tower-type structure in which a plurality of heat dissipation plates are stacked in a vertical direction, so the height dimension is large and the self-weight is considerable, so the first and second heat sinks (30, 40) are prone to tilting sideways due to external force or self-weight when mounted on the base plate (10).

[0053] In particular, when the height of the first and second heat sinks (30, 40) reaches 100mm to 200mm, it is difficult to sufficiently suppress tilting by only combining with the heat pipe (20), and if tilting occurs, the thermal contact state between the base plate (10) and the upper surface of the CPU becomes uneven, causing a problem of reduced cooling performance.

[0054] In addition, when external shocks or vibrations are applied during movement or transportation, the first and second heat sinks (30, 40) may tilt or shake to the side, causing repetitive stress to concentrate at the joint with the heat pipe (20), which can lead to damage to the joint and a decrease in heat transfer performance. Furthermore, since there is no lateral restraint by the fan frame because the fan is not installed, the first and second heat sinks (30, 40) are exposed to external forces without protection, making them prone to tilting or deformation.

[0055] To solve this, the present invention presents a new configuration of a support (100) that physically mutually restrains the lower portions of the first and second heat sinks (30, 40).

[0056] The support member (100) is a structure that connects the lower part of the first heat sink (30) and the lower part of the second heat sink (40) to each other to suppress tilting of the first and second heat sinks (30, 40).

[0057] The material of the support (100) is not particularly limited, but it is preferable to form it from a metal material such as stainless steel (SUS), aluminum alloy, or zinc alloy to ensure sufficient rigidity and durability. The support (100) can be formed by bending a plate, or it can be manufactured by casting or extrusion.

[0058] The position where the support member (100) is connected to the first and second heat sinks (30, 40) is not particularly limited, but it is preferable to connect it to the lower part of the first and second heat sinks (30, 40) to maximize the tilt suppression effect. That is, if the support member (100) is connected to the upper part, there is a risk of interfering with the air passage of the fan mounting part (50), and if it is connected to the middle part, the tilt suppression force may be reduced compared to the lower part due to the lever effect.

[0059] The shape of the support (100) is not particularly limited as long as it is in a shape that can connect the lower parts of the first and second heat sinks (30, 40) to each other.

[0060] For example, it can be implemented in various shapes, such as a simple bar shape that connects directly across the lower portion of the first and second heat sinks (30, 40), a U-shape that connects by bypassing downward from the lower portion, or a frame shape that wraps around the outer side of the lower portion.

[0061] In addition, when multiple supports (100) are provided, they can be spaced apart along the front-rear direction of the first and second heat sinks (30, 40), thereby suppressing the tilting of the first and second heat sinks (30, 40) in the front-rear direction.

[0062] The method of joining between the support (100) and the first and second heat sinks (30, 40) is not particularly limited, so various methods such as screw joining using fasteners (210), rivet joining, welding, bonding, and clip-type detachable joining can be applied.

[0063] When a screw connection method is adopted, assembly and disassembly are easy, which improves maintenance convenience, and when a clip-type detachable connection is adopted, the support (100) can be detached without tools, which increases convenience during work such as replacing a fan (not shown).

[0064] Thus, although the type of fastener (210) is not particularly limited, in order to employ a fastening means that allows for easy adjustment of the fastening torque and visual confirmation of the fastening state, thereby ensuring high assembly reliability, the fastener (210) is preferably a screw-type fastening member such as a bolt, screw, or cap screw having a head portion (211) and a shaft (212).

[0065] In addition, a fastening hole or screw hole is formed at the lower end of the first heat sink (30) or second heat sink (40) to which the fastener (210) is attached, into which the shaft (212) of the fastener (210) can be inserted and fastened.

[0066] In summary, the CPU cooler of the present invention provides the characteristic of maintaining stable cooling performance for a long period of time by efficiently absorbing and discharging heat from the CPU through the organic combination of a base plate (10), a heat pipe (20), first and second heat sinks (30, 40), and a support (100), while suppressing tilting of the heat sink caused by self-weight, external shock, and vibration.

[0067] FIG. 3 is a perspective view illustrating the detailed structure of the support of the present invention.

[0068] Furthermore, the support member (100) of the present invention is preferably specialized in the following detailed structure to increase the coupling stability with respect to the lower portions of the first and second heat sinks (30, 40) and to maximize the tilting suppression effect by arranging a plurality of support members (100) in the front and rear directions.

[0069] Specifically, the support (100) is composed of a first fastening bar (110), a second fastening bar (120), a pair of bent extensions (130), and a connecting bar (140).

[0070] The first fastening bar (110) is a plate-shaped member that contacts the lower portion of the first heat sink (30) and is fastened via a fastener (210), and is formed in a bar shape that extends horizontally along the outer surface of the lower portion of the first heat sink (30).

[0071] A first fastening hole (111) is formed through the first fastening bar (110) through which a fastener (210) passes and is fastened to the lower part of the first heat sink (30).

[0072] The width and thickness of the first fastening bar (110) are designed to sufficiently withstand the fastening force and supporting load generated when fastening the fastener (210), and the thickness can be formed in the range of 1.5 mm to 5.0 mm.

[0073] The second fastening bar (120) is a member that is connected via a fastener (210) by contacting the lower portion of the second heat sink (40) which is spaced apart from the first heat sink (30), and extends parallel to the first fastening bar (110) at a position opposite to the first fastening bar (110).

[0074] A second fastening hole (121) is formed through this second fastening bar (120) through which a fastener (210) passes and is fastened to the lower part of the second heat sink (40).

[0075] The shape and dimensions of the second fastening bar (120) are formed substantially the same as those of the first fastening bar (110) so that the fastening force for the first and second heat sinks (30, 40) is evenly secured.

[0076] In other words, the first and second fastening bars (110, 120) are arranged symmetrically with respect to the spacing direction of the first and second heat sinks (30, 40) and are joined to each of the lower portions of the first and second heat sinks (30, 40) with equal fastening force, thereby ensuring balanced load distribution of the entire support (100).

[0077] In addition, since the first and second fastening bars (110, 120) are independently fastened to the lower portions of the first and second heat sinks (30, 40), even if a minute dimensional deviation occurs due to a difference in thermal expansion amount or assembly tolerance between the first and second heat sinks (30, 40), it can be absorbed so that excessive stress is not concentrated in the fastening portion.

[0078] In addition, since the first and second connecting bars (110, 120) are joined in a state of surface contact with the outer surface of the lower portion of the first and second heat sinks (30, 40), even when vibration is applied to a system in which a CPU cooler is installed, the lower portion of the first and second heat sinks (30, 40) does not move and remains in a stably fixed state.

[0079] A pair of bent extensions (130) are members that are bent downward from the ends of the first fastening bar (110) and the second fastening bar (120), respectively.

[0080] It is preferable for the bending extension (130) to be formed integrally with the first and second fastening bars (110, 120) in terms of securing rigidity, and it can be formed as a single continuous member with the first and second fastening bars (110, 120) by bending the plate material.

[0081] The extension length of the bending extension part (130) is set to correspond to the vertical distance from the first and second fastening bars (110, 120) to the connecting bar (140). As the extension length increases, the position of the connecting bar (140) is lowered, and the overall rigidity of the support (100) is increased, but it must be appropriately designed considering whether there is interference with the base plate (10) or the motherboard.

[0082] The thickness of the bent extension (130) can be formed in the range of 1.5 mm to 5.0 mm so as to sufficiently support the load applied to the support (100).

[0083] These pair of bent extensions (130) are bent downward at each end of the first and second fastening bars (110, 120) and positioned vertically on both sides of the space between the first and second heat sinks (30, 40).

[0084] That is, the bending extension (130) forms the skeleton of the support (100) together with the first and second fastening bars (110, 120) and the connecting bar (140), thereby suppressing deformation in which the lower portions of the first and second heat sinks (30, 40) spread inward or outward and narrow when an external force is applied in any direction.

[0085] In particular, since a pair of bent extensions (130) are located on the left and right sides of the space between the first and second heat sinks (30, 40), they simultaneously restrain the outward tilting of the first and second heat sinks (30, 40) in both left and right directions, and also perform the function of a spacer that maintains a constant spacing so that the distance between the first and second heat sinks (30, 40) does not change.

[0086] At this time, the bending extension (130) may have a chamfer applied to the inner corner of the bending extension (130) to relieve stress concentration occurring between the bending extension (130) and the lower corners of the first and second heat sinks (30, 40) when driving vibration of the fan (not shown) or external impact is applied, and to provide fine fluidity so as to absorb vibration energy.

[0087] That is, by chamfering, the inner corner of the bent extension (130) is formed into an inclined surface, so that the bent extension (130) is joined in a form close to line contact instead of surface contact with the bottom of the heat sink, and when an external force is applied, the bent extension (130) moves slightly around the contact area, thereby obtaining the effect of dispersing and absorbing vibration energy. This chamfering can be applied not only to the connection area between the bent extension (130) and the first and second fastening bars (110, 120), but also to the connection area between the bent extension (130) and the connecting bar (140), and stress concentration at each connection area is simultaneously relieved, thereby improving the vibration absorption performance and durability of the entire support (100).

[0088] The connecting bar (140) is a member that connects the lower ends of a pair of bent extensions (130) to each other, and is formed in the shape of a bar extending horizontally across the pair of bent extensions (130). It is preferable for the connecting bar (140) to be formed integrally with the bent extensions (130) in terms of securing rigidity, and it can be formed as a single member continuous with the bent extensions (130) by bending a plate material. The thickness of the connecting bar (140) can be formed in the range of 1.0 mm to 5.0 mm, and the width can be formed in the range of 3.0 mm to 15.0 mm. The cross-sectional shape of the connecting bar (140) is generally formed as a flat plate, but a bead or a rib may be formed on the cross-section to increase rigidity.

[0089] The connecting bar (140) connects the lower ends of a pair of bent extensions (130), thereby restraining the deformation of the bent extensions (130) from spreading inward or outward due to external force, and serves to maintain the overall shape of the support (100).

[0090] That is, in the absence of the connecting bar (140), the lower ends of the pair of bent extensions (130) are in a free end state and can be easily deformed by external force, but the connecting bar (140) restrains the lower ends of the pair of bent extensions (130), thereby causing the support (100) to form a U-shaped closed-loop frame, and through this, the resistance to tilting load applied to the lower ends of the first and second heat sinks (30, 40) is greatly improved.

[0091] In addition, since the connecting bar (140) is positioned across the lower part of the space between the first and second heat sinks (30, 40), when the support (100) is arranged in multiple numbers at regular intervals in the front-rear direction of the first and second heat sinks (30, 40), the connecting bars (140) can form part of the air passage at the lower part of the first and second heat sinks (30, 40), thereby inducing the heat around the base plate (10) to be discharged downward, which can be expected as an additional effect.

[0092] A support (100) having such a multi-stage bending structure forms an integrated skeletal structure in which the first and second fastening bars (110, 120) are each fastened to the lower ends of the first and second heat sinks (30, 40), and a pair of bending extensions (130) stand vertically and are restrained at their lower ends by a connecting bar (140), thereby providing multi-directional restraint characteristics that simultaneously resist left-right tilting loads, front-back shaking loads, and inner-outer spreading loads applied to the first and second heat sinks (30, 40).

[0093] In addition, since it can be manufactured by bending a single component, it has the advantage of ensuring uniform rigidity without welds or fasteners and simplifying the manufacturing process.

[0094] These supports (100) can be formed by arranging multiple supports in the front-rear direction or by forming one with a wide area that extends a predetermined length in the front-rear direction of the first and second heat sinks (30, 40).

[0095] FIG. 3 illustrates an embodiment in which a plurality of supports (100) are spaced apart in the front-rear direction, and FIG. 7 and FIG. 8 illustrate an embodiment in which one support (100) is applied with a predetermined length in the front-rear direction of the first and second heat sinks (30, 40).

[0096] In summary, the support (100) of the present invention, despite having a simple structure, simultaneously possesses high resistance to multi-directional loads and excellent manufacturability, thereby providing characteristics that fundamentally improve the structural reliability of a dual-tower type CPU cooler.

[0097] The first and second fastening holes (111, 121) described above may be formed as simple circular through holes, but when the first and second heat sinks (30, 40) undergo thermal expansion due to heat transferred through the heat pipe (20) during the operation of the CPU cooler, and when a fine dimensional change occurs along the extension direction of the first and second fastening bars (110, 120), such thermal expansion is not freely allowed when the fastener (210) is strongly fixed to the circular fastening hole, so repetitive stress is concentrated in the fastening part, and this may lead to damage to the fastening part or loosening of the fastener (210) during long-term use.

[0098] Additionally, when self-weight or external impact is applied to the first and second heat sinks (30, 40), the first and second heat sinks (30, 40) may tilt slightly or exhibit a tendency to deviate from the fastening bar (110, 120). In the case of a circular fastening hole structure, the fastener (210) strongly resists this behavior, causing stress to concentrate around the fastening hole and potentially causing the connection between the first and second heat sinks (30, 40) and the fastening bar (110, 120) to become misaligned.

[0099] In particular, in an environment where vibration caused by the operation of a fan (not shown) is continuously applied, the two problems above act in combination, increasing the possibility of fatigue failure of the fastening part and causing a problem where the thermal contact state between the first and second heat sinks (30, 40) and the base plate (10) becomes uneven.

[0100] To solve this problem, as shown in FIGS. 4 and 5, a vibration-absorbing fastening structure is presented in which the first and second fastening holes (111, 121) are formed as elongated holes and an annular bushing (220) and an elastic washer (230) are combined.

[0101] FIG. 4 is a longitudinal section view in the short axis direction around the first and second fastening holes of the present invention, and FIG. 5 is a cross-sectional view AA of FIG. 4.

[0102] Specifically, the first and second fastening holes (111, 121) are each formed as long holes with a long axis formed along the extension direction of the first and second fastening bars (110, 120).

[0103] The elongated hole is a structure that allows the fastener (210) to move relative within a certain range along the extension direction of the fastening bar (110, 120), that is, the thermal expansion direction and tilting behavior direction of the first and second heat sinks (30, 40), and can be said to be applied to fundamentally resolve the problem of stress concentration and joint damage occurring in the circular fastening hole.

[0104] The length of the major axis of the long hole can be set by comprehensively considering the expected amount of thermal expansion, assembly tolerance, and allowable flow rate, and the length of the minor axis is set to correspond to the outer diameter of the annular bush (220).

[0105] A gap of δ is formed between both ends of the long axis direction of the long hole and the annular bush (220), thereby securing a space in which the fastener (210) and the annular bush (220) can move relative to each other along the long axis direction.

[0106] At this time, if the size of δ is too small, it may not allow sufficient thermal expansion and tilting behavior, and if it is too large, the flow amount of the fastener (210) may become excessive and the fastening stability may be reduced, so it can be appropriately set within the range of 0.1 mm to 15.0 mm depending on the specifications and design conditions of the CPU cooler to be applied.

[0107] The annular bush (220) is a hollow cylindrical member fitted onto the outer surface of the fastener (210) and is formed of an elastic material such as rubber, silicone, or urethane.

[0108] These annular bushes (220) are formed of an elastic material, so they act as a cushion between the fastener (210) and the inner surface of the elongated hole, thereby also having the effect of suppressing vibration and shock from being directly transmitted to the first and second heat sinks (30, 40).

[0109] The outer diameter of the annular bush (220) is set to be in close contact with the inner circumference in the direction of the short axis of the long axis, corresponding to the short axis width of the long axis, and the inner diameter is set to be in close contact with the outer circumference of the fastener (210), corresponding to the outer diameter of the shaft (212) of the fastener (210).

[0110] It is preferable that the axial length of the annular bush (220) be set to correspond to the thickness of the elongated hole, that is, the thickness of the first and second fastening bars (110, 120). If the axial length is too short, the contact area with the inner surface of the elongated hole is reduced, thereby lowering the short-axis restraining force, and if it is too long, the annular bush (220) may protrude out of the elongated hole when the fastener (210) is fastened, thereby compromising the fastening stability. Therefore, it is preferable that it be designed within a range corresponding to the thickness of the fastening bars (110, 120).

[0111] These annular bushes (220) form an assembly together with fasteners (210) and slide freely within a range of δ in the direction of the major axis of the hole, but elastically adhere to the inner surface of the hole in the direction of the minor axis to restrict the movement of the fasteners (210) in the direction of the minor axis.

[0112] In other words, the annular bush (220) performs a directional flow control function that allows the degree of freedom in the long axis direction while restricting the degree of freedom in the short axis direction, and also prevents direct metal contact between the fastener (210) and the inner surface of the elongated hole due to the cushioning properties unique to the elastic material, thereby suppressing plastic deformation and wear of the area around the elongated hole caused by impact load.

[0113] The elastic washer (230) is a ring-shaped member interposed between the head portion (211) of the fastener (210) and the surface of the first and second fastening bars (110, 120), and is formed of an elastic material such as rubber, silicone, or urethane. Since the elastic washer (230) is formed of an elastic material, a constant elastic restoring force is maintained even after the fastener (210) is fastened, thereby also obtaining the effect of suppressing the loosening of the fastener (210) due to vibration or impact.

[0114] The inner diameter of the elastic washer (230) is formed to be smaller than the outer diameter of the head portion (211) of the fastener (210), so that the head portion (211) of the fastener (210) cannot penetrate the elastic washer (230) and rests on the elastic washer (230).

[0115] The outer diameter (D) of the elastic washer (230) is formed to be larger than the short-width (W) of the elongated hole, so that the elastic washer (230) does not sink into the elongated hole and remains in a state of being stretched across the surface of the first and second fastening bars (110, 120).

[0116] At this time, as the outer diameter (D) of the elastic washer (230) is formed to be sufficiently larger than the short-width (W) of the elongated hole, the contact area of ​​the elastic washer (230) with the surface of the fastening bar (110, 120) is widened, so that the axial load of the fastener (210) is evenly distributed on the surface of the fastening bar (110, 120). Therefore, it is desirable that the outer diameter (D) of the elastic washer (230) be set within a range where a sufficient contact area can be secured according to design conditions.

[0117] If the thickness of the elastic washer (230) is too thin, it is difficult to expect a sufficient vibration absorption effect, and if it is too thick, the fastening depth of the fastener (210) may be reduced and the fastening force may be reduced, so it is appropriately set according to the specifications of the fastener (210) and the required vibration absorption performance.

[0118] The elastic washer (230) is compressed and deformed between the head portion (211) and the surface of the fastening bar when the fastener (210) is fastened, and performs the function of absorbing axial vibration.

[0119] Furthermore, the elastic washer (230) is combined with the longitudinal sliding allowance function of the annular bush (220), so that the axial vibration absorption function between the head portion (211) of the fastener (210) and the surface of the fastening bar (110, 120) is continuously performed without interruption even in situations where relative movement in the longitudinal direction occurs.

[0120] In other words, the elastic washer (230) works organically with the annular bush (220) to complete a composite function fastening structure that simultaneously allows for flow in the longitudinal direction and absorbs axial vibration.

[0121] Looking at the operation flow of the structure described above, first, the annular bushing (220) is fitted onto the outer surface of the shaft (212) of the fastener (210) and inserted into the elongated hole (111, 121), and the fastener (210) is fastened to the lower part of the first and second heat sinks (30, 40) with an elastic washer (230) interposed between the head portion (211) of the fastener (210) and the surface of the fastening bar (110, 120).

[0122] In this state, the outer surface of the annular bush (220) is elastically attached to the inner surface in the short axis direction of the elongated hole, so the fastener (210) is restricted from flowing in the short axis direction and can move freely only within the δ range in the long axis direction.

[0123] When the CPU cooler operates and thermal expansion occurs in the first and second heat sinks (30, 40), or when the first and second heat sinks (30, 40) attempt to slightly deviate in the longitudinal direction relative to the fastening bar (110, 120) due to external impact and tilting behavior, the annular bushing (220) and fastener (210) assembly slides in the longitudinal direction within the elongated hole to naturally allow this, thereby preventing stress from concentrating in the fastening part.

[0124] At the same time, when driving vibrations of the fan (not shown) or external vibrations are transmitted in the axial direction of the fastener (210), the elastic washer (230) absorbs vibration energy by repeatedly compressing and restoring between the head portion (211) and the surface of the fastening bar (110, 120).

[0125] With this structure, the assembly consisting of an annular bush (220) and a fastener (210) moves freely relative to each other within a range of δ in the direction of the long axis of the hole, thereby allowing for dimensional changes due to thermal expansion, and the elastic washer (230) absorbs axial vibration of the fastener (210), thereby preventing fatigue failure of the fastening part, and these two functions are performed simultaneously, thereby providing the advantage of maintaining a stable fastening state for a long period of time.

[0126] FIG. 6 illustrates the structure of the guide groove and guide projection of the present invention, where the left side is a plan view of the surface around the elongated hole of the fastening bar and the right side is a plan view of the lower surface of the elastic washer.

[0127] Furthermore, the elastic washer (230) described above is structured to allow sliding in the long axis direction of the long hole (111, 121), and even after the fastener (210) is fastened, if an external force in the long axis direction is applied, it moves together with the fastener (210) within the long hole. In this process, if the elastic washer (230) rotates on the surface of the fastening bar (110, 120) or deviates in the short axis direction, the vibration absorption function of the elastic washer (230) is reduced, and the contact area between the elastic washer (230) and the surface of the fastening bar (110, 120) becomes uneven, causing the axial load to be unevenly distributed, which may result in a problem of reduced durability of the fastening part.

[0128] In addition, if the elastic washer (230) is displaced from its proper position and a portion of the opening of the elongated hole (111, 121) is exposed, foreign matter may enter, hindering the sliding motion, and the elastic washer (230) itself may wear out or deform during the repetitive flow process, which may reduce long-term vibration absorption performance and fastening stability.

[0129] To prevent this, the present invention additionally provides a guide groove (112) on the surface around the long axis of the elongated hole (111, 121) of the first and second fastening bars (110, 120) as shown in FIG. 6, and a guide projection (231) on the lower surface of the elastic washer (230).

[0130] Specifically, a guide groove (112) extending along the direction of the long axis is formed on the surface around the long axis of the elongated hole (111, 121) in the first and second fastening bars (110, 120).

[0131] The guide groove (112) extends parallel to the long axis direction of the elongated hole (111, 121) and serves to guide the sliding path for the guide projection (231) of the elastic washer (230) to be described later. Its cross-sectional shape can be formed in a shape complementary to the guide projection (231), such as a square, a semicircle, or a trapezoid.

[0132] The extended length of the guide groove (112) is set to correspond to the length of the long axis of the elongated hole (111, 121) so as to cover the entire sliding range of the elastic washer (230).

[0133] In response to this, on the lower surface of the elastic washer (230), guide projections (231) are formed on both sides in the long axis direction, with the fastener through hole (232) in between, which are inserted into the guide groove (112) and can slide along the long axis direction.

[0134] It is preferable that the guide projection (231) be formed integrally with the elastic washer (230) and be formed in a shape corresponding to the cross-sectional shape of the guide groove (112) so that it slides smoothly in the long axis direction within the guide groove (112), but its flow is restricted in the short axis direction and rotational direction.

[0135] The height of the guide projection (231) is set to correspond to the depth of the guide groove (112), and is designed so that the lower surface of the elastic washer (230) can be in close contact with the surface of the fastening bar (110, 120) when the guide projection (231) is fully inserted into the guide groove (112).

[0136] Specifically, when the fastener (210) is fastened, the guide projection (231) of the elastic washer (230) is inserted into the guide groove (112) of the fastening bar (110, 120), and the elastic washer (230) is seated in the correct position. Subsequently, when the fastener (210) and the annular bushing (220) assembly slide in the longitudinal direction due to the thermal expansion or tilting behavior of the first and second heat sinks (30, 40), the elastic washer (230) is also guided along the guide groove (112) by the guide projection (231) and moves together in the longitudinal direction.

[0137] In this process, the side of the guide projection (231) contacts the inner wall of the guide groove (112) and restricts flow and rotation in the short-axis direction, so the elastic washer (230) always maintains a position covering the opening of the elongated hole (111, 121) even while sliding.

[0138] In this way, the guide groove (112) and the guide projection (231) are coupled together, so that the elastic washer (230) is allowed only to slide in the long axis direction and rotation and movement in the short axis direction are restricted, so that it always maintains a fixed position covering the opening of the elongated hole (111, 121).

[0139] Through this, the vibration absorption function of the elastic washer (230) is continuously and stably exerted, and the long-term durability of the fastening part is secured, as well as the intrusion of foreign matter into the area around the elongated hole (111, 121) is prevented, so the reliability of the sliding operation can be maintained for a long time.

[0140] FIG. 7 is a perspective view illustrating a first modified embodiment of the support of the present invention, and FIG. 8 is a perspective view illustrating the state in which the first and second heat sinks are mounted on the support of FIG. 7.

[0141] Furthermore, the support (100) of the present invention may be implemented as a modified embodiment in which a first fastening bar (110), a second fastening bar (120), a pair of bent extensions (130), and a connecting bar (140) are formed by extending a predetermined length in the front-rear direction of the first and second heat sinks (30, 40), as shown in FIGS. 7 and 8.

[0142] In this way, if the support member (100) is formed by extending it to a predetermined length in the front-rear direction, a single support member (100) can achieve a front-rear tilt suppression effect equivalent to that of arranging multiple support members (100) in the front-rear direction, thereby reducing the number of parts and simplifying the assembly process.

[0143] At this time, the first fastening hole (111) and the second fastening hole (121) are formed in pairs around both ends along the front-rear direction of each fastening bar (110, 120) in correspondence with the support member (100) being extended by a predetermined length in the front-rear direction of the first and second hex sinks (30, 40), and are fastened with fasteners (210) on both sides in the front-rear direction, thereby restricting the movement of the support member (100) in the front-rear direction and dispersing the load applied to the fastening part.

[0144] In addition, a through hole (140a) is formed in the central portion of the connecting bar (140) in the thickness direction.

[0145] As shown in FIG. 7, in a structure where the support (100) occupies a large area in the front-rear direction, if the connecting bar (140) is formed in a closed shape without a through hole (140a), the connecting bar (140) blocks a large area of ​​the lower part of the space between the first and second heat sinks (30, 40), thereby blocking the path for heat around the base plate (10) to be discharged downward and causing the problem of the weight of the entire support (100) to increase excessively.

[0146] To solve this, a through hole (140a) is formed in the central portion of the connecting bar (140), thereby securing a heat exhaust path and preventing a decrease in cooling performance. Furthermore, the connecting bar (140) is given fluidity that allows the portions on both sides to independently undergo fine elastic deformation with respect to the through hole (140a), so that when driving vibrations of a fan (not shown) or external impacts are applied, vibration energy is dispersed and absorbed in the portion of the connecting bar (140).

[0147] That is, the support (100) having a large surface area in the front-rear direction of the first and second heat sinks (30, 40) behaves like a rigid body so that vibrations can be transmitted as they are, but the through hole (140a) suppresses the rigid behavior of the connecting bar (140), thereby ensuring structural rigidity and vibration absorption performance complementarily.

[0148] In this way, by providing a support (100) and a through hole (140a) that are extended for a predetermined length in the front-rear direction of the first and second heat sinks (30, 40), it is possible to obtain the effect of simultaneously suppressing tilting in the front-rear and left-right directions with a single support (100) while minimizing the reduction in cooling performance and vibration amplification.

[0149] FIG. 9 is a perspective view illustrating a second modified embodiment of the support of the present invention.

[0150] As can be seen from FIG. 9, the support (100) of the present invention may additionally include a reinforcing plate (150) to suppress deformation in which a pair of bent extensions (130) spread inward or outward due to external impact or repeated vibration, and to increase the structural rigidity of the entire support (100).

[0151] The reinforcing plate (150) is a plate-shaped member that connects between a pair of bent extensions (130) and extends parallel to the connecting bar (140), and is coupled to the inner surface of the pair of bent extensions (130). The reinforcing plate (150) can be formed integrally with the bent extensions (130), or it can be manufactured separately and then joined by welding or fastening.

[0152] These reinforcing plates (150) may be connected across the middle of a pair of bent extensions (130), but in order to maximize the torsional rigidity of the support (100) and effectively distribute the stress concentrated around the connection point with the first and second fastening bars (110, 120), they may be connected across the pair of bent extensions (130) at the upper part of the bent extensions (130), that is, at a position adjacent to the first and second fastening bars (110, 120), as shown in FIG. 9, just as they connect the first and second fastening bars (110, 120).

[0153] By connecting the reinforcing plate (150) across the pair of bending extensions (130), a double restraint structure is formed in which both the upper and lower sides of the bending extensions (130) are restrained together with the connecting bar (140), thereby greatly improving the torsional rigidity and bending rigidity of the support (100).

[0154] In addition, an opening (151) penetrating in the thickness direction is formed in the central portion of the reinforcing plate (150).

[0155] The opening (151) is formed so that the reinforcing plate (150) is installed across a pair of bent extensions (130), thereby solving the problem of the gap between the first and second heat sinks (30, 40) being blocked by the reinforcing plate (150).

[0156] That is, if the reinforcing plate (150) is installed in a manner that completely blocks the gap space without an opening (151), the reinforcing plate (150) acts as a rigid structure that strongly connects a pair of bent extensions (130), so that the driving vibration of the fan (not shown) or external shock is evenly transmitted through the reinforcing plate (150) to the entire support (100), and the entire support (100) resonates as a whole, which may cause a problem in which the vibration is amplified.

[0157] Therefore, by forming an opening (151), the vibration transmission path through the reinforcing plate (150) is blocked, thereby preventing resonance and vibration amplification problems, and while maintaining the rigidity reinforcement effect of the reinforcing plate (150), an air flow path is secured, thereby preventing a decrease in cooling performance.

[0158] In addition, the opening (151) also serves to increase the durability of the reinforcing plate (150) itself by dispersing the stress concentrated in the center of the reinforcing plate (150).

[0159] The shape of the opening (151) can be formed in various ways, such as circular, elliptical, or rectangular, and the size of the opening (151) can be appropriately set according to design conditions within a range that can maintain the rigidity of the reinforcing plate (150).

[0160] When looking at the operation flow of the reinforcing plate (150) and the opening (151), when driving vibrations of a fan (not shown) or external shocks are transmitted to the support (100), the reinforcing plate (150) connects between a pair of bent extensions (130) to restrain the inner and outer deformation of the bent extensions (130), and the opening (151) penetrates the center of the reinforcing plate (150), thereby dividing the vibration transmission path through the reinforcing plate (150) and dispersing and damping the vibration energy around the opening (151).

[0161] That is, the reinforcing plate (150) performs a rigidity reinforcement function that restrains the deformation of the bent extension (130), while the opening (151) performs a function that prevents vibration from being amplified and transmitted to the entire support (100) by suppressing the rigid behavior of the reinforcing plate (150), thereby achieving mutually complementary rigidity reinforcement and vibration suppression.

[0162] By providing a reinforcing plate (150) and an opening (151) in this manner, the structural rigidity of the support (100) can be increased, while providing characteristics that minimize vibration amplification, blockage of air passages, and weight increase.

[0163] Furthermore, the support member (100) of the present invention is based on a structure in which rigidity is enhanced by the addition of a reinforcing plate (150), and by optimizing the shape of a pair of bent extensions (130) and a connecting bar (140), the rigidity reinforcement effect can be further enhanced while simultaneously improving vibration absorption performance.

[0164] Specifically, a pair of bent extensions (130) have an outer surface formed as a straight line and an inner surface formed as an arched curve, so that the thickness between the inner and outer sides is formed differently.

[0165] By forming the outer surface of the bent extension part (130) as a straight line, interference with the outer surface of the first and second heat sinks (30, 40) can be prevented and the assembly space can be minimized.

[0166] In addition, by forming the inner surface into an arched curve, the cross-section of the bent extension (130) becomes thicker toward the center, so that the stress concentrated at the joint with the reinforcing plate (150) is distributed along the arched curve, thereby preventing local deformation and damage of the bent extension (130).

[0167] That is, in a situation where the load transmitted to the bent extension (130) increases due to the addition of the reinforcing plate (150), the arched curved surface of the inner side serves to compensate for this increase in load and enhance the durability of the bent extension (130).

[0168] Additionally, a slit (141) is formed through the connecting bar (140) along the length direction.

[0169] The slit (141) is formed in the shape of an elongated groove extending along the length direction of the connecting bar (140) and penetrates in the thickness direction of the connecting bar (140).

[0170] In a structure with an added reinforcing plate (150), the overall rigidity of the support (100) is increased, while the flexibility to absorb vibration energy may be reduced. By forming a slit (141), the connecting bar (140) is provided with appropriate elastic deformation room, allowing the vibration energy transmitted through the reinforcing plate (150) to be absorbed and dampened at the connecting bar (140) portion.

[0171] The width and length of the slit (141) are set considering the balance between the required stiffness and vibration absorption performance, and as the length of the slit (141) increases the vibration absorption effect, the stiffness of the connecting bar (140) may decrease, so they are appropriately set according to the applied design conditions.

[0172] When looking at the operation flow of the slit (141), when the driving vibration of the fan (not shown) or external shock is transmitted to the support (100) and the vibration energy transmitted to the bending extension (130) through the reinforcing plate (150) reaches the connecting bar (140), the two sides of the connecting bar (140) independently undergo fine elastic deformation with respect to the slit (141) and disperse and absorb the vibration energy.

[0173] That is, when there is no slit (141), the connecting bar (140) behaves as a rigid body and the vibration is transmitted directly to the opposite bending extension (130), but when the slit (141) is formed, the connecting bar (140) behaves flexibly around the slit (141), blocking the vibration transmission path and attenuating the energy.

[0174] In this way, by providing the arched inner surface of the bent extension (130) and the slit (141) of the connecting bar (140) together with the reinforcing plate (150), the support (100) can simultaneously possess high structural rigidity and vibration absorption performance, thereby strengthening long-term stable support characteristics.

[0175] As explained above, the configuration and operation of the construction material ordering system based on the standardization of non-standard material names according to the present invention have been described and drawn in the above description and drawings; however, this is merely an example, and the concept of the present invention is not limited to the above description and drawings. It is understood that various changes and modifications are possible within the scope of the technical concept of the present invention. Explanation of the symbols

[0176] 10: Base plate 20: Heat pipe 30: 1st Heat Sink 40: 2nd Heat Sink 50: Fan mounting section 100: Support bracket 110: First fastening bar 111: First fastening hole 112: Guide Home 120: Second Fastening Bar 121: Second fastening hole 130: Bending extension 140: Connecting bar 140a: Through hole 141: Slit 150: Reinforcement plate 151: Opening 210: Fastener 211: Head 212: Shaft 220: Ring bush 230: Elastic washer 231: Guide projection 232: Fastener penetration hole

Claims

Claim 1 A dual-tower type CPU cooler equipped with a support that suppresses tilting of a heat sink, comprising: a base plate that contacts a CPU to absorb heat; a plurality of heat pipes coupled to the base plate to receive heat; and a first heat sink and a second heat sink connected to the plurality of heat pipes to release heat. and, a support comprising: a first fastening bar having a first fastening hole formed through it to contact the lower end of the first heat sink and fasten via a fastener, a second fastening bar having a second fastening hole formed through it to contact the lower end of the second heat sink and fasten via a fastener, a pair of bent extensions each bent downward from the ends of the first and second fastening bars to suppress tilting of the first and second heat sinks; and a connecting bar connecting the lower ends of the pair of bent extensions. The first and second fastening holes are each formed as elongated holes with a long axis formed along the extension direction of the first and second fastening bars. An annular bushing made of an elastic material is fitted onto the outer surface of the fastener and adheres to the inner surface in the direction of the short axis of the elongated hole. Between the head of the fastener and the surface of the first and second fastening bars, the fastener head A CPU cooler characterized by having an elastic washer interposed having an inner diameter smaller than the outer diameter and an outer diameter larger than the major axis width of the elongated hole, wherein the annular bushing and the fastener move relative to each other in the major axis direction of the elongated hole and axial vibration absorption by the elastic washer is simultaneously achieved. Claim 2 A CPU cooler according to claim 1, wherein the first and second heat sinks are each spaced apart from each other and arranged side by side in a tower-like state formed by stacking a plurality of heat dissipation plates in a vertical direction, and a fan mounting portion for mounting a fan is formed in the spaced-apart space between the first and second heat sinks. Claim 3 A CPU cooler according to claim 1, wherein a guide groove extending along the long axis direction of the first and second fastening holes is formed on the surface around the long axis of the long holes in the first and second fastening bars, and guide protrusions that are inserted into the guide grooves and capable of sliding along the long axis direction are formed on both sides of the long axis direction with the fastener through hole in between on the lower surface of the elastic washer, thereby restricting the rotation and short axis direction movement of the elastic washer. Claim 4 A CPU cooler according to claim 1, wherein the first fastening bar, the second fastening bar, a pair of bent extension parts, and the connecting bar are formed to be extended by a predetermined length in the front-rear direction of the first and second heat sinks, and a through hole formed in the thickness direction is formed in the central part of the connecting bar. Claim 5 A CPU cooler according to claim 4, wherein the support member further comprises a reinforcing plate extending parallel to the connecting bar and connecting between the pair of bent extensions, wherein an opening penetrating in the thickness direction is formed in the central portion of the reinforcing plate, and wherein the pair of bent extensions have an outer surface formed as a straight line and an inner surface formed as an arched curved surface, so that the thickness between the inner and outer sides is formed differently, and wherein a slit penetrating along the length direction is formed in the connecting bar. Claim 6 delete Claim 7 delete

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