JP4770207B2 - Pump and liquid supply apparatus having the same - Google Patents

Pump and liquid supply apparatus having the same Download PDF

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JP4770207B2
JP4770207B2 JP2005066994A JP2005066994A JP4770207B2 JP 4770207 B2 JP4770207 B2 JP 4770207B2 JP 2005066994 A JP2005066994 A JP 2005066994A JP 2005066994 A JP2005066994 A JP 2005066994A JP 4770207 B2 JP4770207 B2 JP 4770207B2
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blade
pump
impeller
discharge port
refrigerant
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JP2006250019A (en
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英稔 植田
政昭 西方
敏輔 酒井
晴海 福木
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Panasonic Corp
Panasonic Electric Works Co Ltd
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Matsushita Electric Works Ltd
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Description

モータにより駆動され、液体を吸入して吐出するポンプ及びそれを備えた液体供給装置に関する。   The present invention relates to a pump that is driven by a motor and sucks and discharges liquid, and a liquid supply apparatus including the pump.

ポンプにおいては、主として磁界を発生させるステータやそのステータを制御する制御部からなるモータ部と、ステータで発生された磁界により駆動され水等の液体を吸排する羽根車からなるポンプ部と、モータ部とポンプ部を隔離する仕切板とから構成される。   In the pump, a motor unit mainly including a stator that generates a magnetic field and a control unit that controls the stator, a pump unit that is driven by a magnetic field generated by the stator and sucks and discharges liquid such as water, and a motor unit And a partition plate that separates the pump part.

この中でポンプ部は羽根車によって吸入した液体の圧力を高めて吐出する。例えば、遠心ポンプでは羽根車は複数の羽根が羽根への負荷を減らすため回転方向に対して後傾するように全体に湾曲した状態で固定されている。また、渦流ポンプでは複数の羽根と各羽根によって仕切られた溝が羽根車外縁部に設けられている。   Among these, the pump unit increases the pressure of the liquid sucked by the impeller and discharges it. For example, in a centrifugal pump, the impeller is fixed in a state of being curved as a whole so that a plurality of blades tilt backward with respect to the rotation direction in order to reduce the load on the blades. In the vortex pump, a plurality of blades and grooves partitioned by the blades are provided on the outer edge of the impeller.

しかしながら、遠心ポンプの羽根形状では遠心力によって圧力を高めるので、より高圧力の液体を吐出するには回転数を上げるか羽根車外形を大きくする必要があった。   However, since the pressure is increased by centrifugal force in the blade shape of the centrifugal pump, it has been necessary to increase the rotational speed or to increase the outer shape of the impeller in order to discharge higher pressure liquid.

また、渦流ポンプの羽根形状ではポンプケースと羽根車の摩擦流で圧力を高めるので遠心ポンプより高圧力の液体を吐出させることが出来るが軸近傍の液体循環がないため、軸と羽根車を固定して軸を回転させてボールベアリング等の軸受を用いるので軸受磨耗によるポンプ寿命が問題となっていた。   In addition, the vortex pump blade shape increases the pressure by the friction flow between the pump case and the impeller, so that higher pressure liquid can be discharged than the centrifugal pump, but there is no liquid circulation near the shaft, so the shaft and impeller are fixed. Since the shaft is rotated and a bearing such as a ball bearing is used, the pump life due to bearing wear has been a problem.

このため遠心ポンプの羽根形状において羽根が外縁部端部で羽根車の回転方向とは逆向き方向に窪んだ凹部が形成されたポンプが提案されている（例えば特許文献１参照）。   For this reason, a pump has been proposed in which the blades of the centrifugal pump have recesses that are recessed in the direction opposite to the direction of rotation of the impeller at the edge of the outer edge (see, for example, Patent Document 1).

上記の羽根車を用いると、軸受の長寿命化が比較的簡単な遠心ポンプでありながらより高圧力の液体を吐出することが出来る。
特開２００１−８２３８３号公報 When the above-described impeller is used, a higher-pressure liquid can be discharged while the centrifugal pump has a relatively simple bearing life.
JP 2001-82383 A

しかしながら前記従来の技術の（特許文献１）に記載のポンプでは、羽根の窪んだ凹部に圧力の集中が起こってしまい、特に大流量のポンプ出力が不要な低流量ポンプにおいては通常羽根車最外周部の接線上にある吐出口へは効率良く圧力の伝達が出来ずに羽根車内の高圧力を吐出させることが困難な場合があった。   However, in the pump described in the above-mentioned prior art (Patent Document 1), pressure concentration occurs in the recessed portion where the blade is recessed, and the outermost periphery of the impeller is usually the outermost periphery of the low-flow pump that does not require a high-flow pump output. In some cases, it was difficult to discharge high pressure in the impeller without efficiently transmitting pressure to the discharge port on the tangent line of the section.

また、羽根車から与えられる圧力エネルギーは小さいため、高圧力の液体を吐出するには羽根車の回転数を上げる必要があり、軸及び軸を支える摺動部分の寿命の低下にもつながっていた。   Moreover, since the pressure energy given from the impeller is small, it is necessary to increase the rotation speed of the impeller in order to discharge high-pressure liquid, leading to a reduction in the life of the shaft and the sliding portion that supports the shaft. .

本発明はこのような従来の課題を解決するものであり、小型で圧力損失の少ない高圧力の液体の吐出を得ることができ、かつ長寿命のポンプ及びそれを備えた液体供給装置を提供することを目的とする。   The present invention solves such a conventional problem, and provides a long-life pump and a liquid supply apparatus including the pump that can obtain a small-sized and high-pressure liquid discharge with little pressure loss. For the purpose.

本発明は上記目的を達成するために、液体を吸排する羽根車を内蔵したポンプ部と、液体を吸入する吸入口と液体を吐出する吐出口が接続されポンプ部を収納するポンプケースと、羽根車を駆動するモータ部とを有し、前記羽根車は、前記吸入口からの液体が前記羽根車の中心に導入されると共に、前記中心より外周に向かって放射状に形成された第１の羽根を備え、前記第１の羽根の外周部であって羽根車の側面部に第２の羽根を設け、前記第２の羽根の外周に吐出口を設けると共に、前記吐出口はポンプケースの内側に開口した入り口部の内面の最上部と最下部の間の回転軸方向に沿った高さ寸法が第２の羽根の上面と下面の間の高さ寸法より小さく、かつ吐出口内面の最上部を第２の羽根の上面より低い位置に配置し吐出口内面の最下部を第２の羽根の下面より高い位置に配置したことを特徴としている。 For the present invention to achieve the above object, a pump case for accommodating a pump unit with a built-impeller suction and discharge of liquid, the pump unit discharge opening is connected for discharging a suction port and a liquid inhaling liquids, A motor unit for driving the impeller , wherein the impeller is configured such that liquid from the suction port is introduced into the center of the impeller and is formed radially from the center toward the outer periphery . comprising a blade, the first a peripheral portion of the blade is provided with a second blade on the side surface of the impeller, provided with a discharge opening on the outer periphery of the second blade, the inside of the discharge port pump case The height dimension along the rotation axis direction between the uppermost portion and the lowermost portion of the inner surface of the inlet portion opened in the upper portion is smaller than the height dimension between the upper surface and the lower surface of the second blade, and the uppermost portion of the inner surface of the discharge port Placed at a position lower than the upper surface of the second blade, and the bottom of the inner surface of the discharge port Is characterized in that the disposed higher than the lower surface of the second blade position.

この構成により、羽根車中心部から吸入した液体を第１の羽根による遠心力で圧力を高めながら第２の羽根まで導き、第２の羽根とポンプケースとの摩擦流によりさらに圧力を高めるので羽根車内の高圧力の液体を羽根車外周部にある吐出口から効率良く吐出させることができ、しかも羽根車中心部から吸入するので軸受と軸との間に液体による潤滑作用で摺動性を高めることができ、長寿命化が図れるという作用が達成できる。   With this configuration, the liquid sucked from the impeller center is guided to the second blade while increasing the pressure by the centrifugal force of the first blade, and the pressure is further increased by the frictional flow between the second blade and the pump case. High pressure liquid in the vehicle can be efficiently discharged from the discharge port on the outer periphery of the impeller, and since it is sucked from the center of the impeller, slidability is improved by the lubricating action of the liquid between the bearing and the shaft. Thus, the effect of extending the life can be achieved.

本発明は、小型で圧力損失の少ない高圧力の液体の吐出を得ることができ、かつ長寿命のポンプ及びそれを備えた液体供給装置を提供することができるという効果を奏する。   The present invention is advantageous in that it is possible to provide a small-sized high-pressure liquid discharge liquid with little pressure loss and a long-life pump and a liquid supply apparatus including the pump.

本発明の実施の形態は、液体を吸排する羽根車を内蔵したポンプ部と、所定の場所に液体を吸入する吸入口と液体を吐出する吐出口が接続されポンプ部を収納するポンプケースと、羽根車を駆動するモータ部とを有し、前記羽根車の中心より所定の距離から所定の長さと幅をもつ第１の羽根を備え、前記第１の羽根の外周部であって羽根車の側面部に所定の長さと高さをもった第２の羽根を設けたものである。   An embodiment of the present invention includes a pump unit incorporating an impeller for sucking and discharging liquid, a pump case for storing a pump unit by connecting a suction port for sucking liquid and a discharge port for discharging liquid to a predetermined place, A motor unit for driving the impeller, the first impeller having a predetermined length and width from a predetermined distance from the center of the impeller, and an outer peripheral part of the first impeller, A second blade having a predetermined length and height is provided on the side surface.

これにより、羽根車中心部から吸入した液体を第１の羽根による遠心力で圧力を高めながら第２の羽根まで導き、第２の羽根とポンプケースとの摩擦流によりさらに圧力を高めるので羽根車内の高圧力の液体を羽根車外周部にある吐出口から効率良く吐出させることができるポンプを提供することができる。   As a result, the liquid sucked from the impeller center is guided to the second blade while increasing the pressure by the centrifugal force of the first blade, and the pressure is further increased by the frictional flow between the second blade and the pump case. It is possible to provide a pump that can efficiently discharge the high-pressure liquid from the discharge port in the outer peripheral portion of the impeller.

また、前記第２の羽根は、羽根車の中心線に対して羽根車の回転方向と反対側に所定の角度で傾斜して配置してもよい。   The second blade may be disposed at a predetermined angle with respect to the center line of the impeller on the side opposite to the rotation direction of the impeller.

これにより、第２の羽根とポンプケースとの摩擦流による負荷抵抗を下げて渦の回転を高めることができ、さらに高圧力の液体を吐出させることができる。   As a result, the load resistance due to the frictional flow between the second blade and the pump case can be reduced, the rotation of the vortex can be increased, and a liquid with a higher pressure can be discharged.

また、前記第１の羽根の吸入口側に第１の羽根を覆う覆板を配置してもよい。   A cover plate that covers the first blade may be disposed on the suction port side of the first blade.

これにより、第１の羽根上面からの液体の漏れによる圧力損失を防ぎ第２の羽根に導かれる液体の圧力を高めることができる。   Thereby, pressure loss due to liquid leakage from the upper surface of the first blade can be prevented, and the pressure of the liquid guided to the second blade can be increased.

また、前記ポンプケースは、内面と第２の羽根の間隙を羽根車に第２の羽根が接続されたところが最も狭い所定の幅に形成してもよい。   In the pump case, the gap between the inner surface and the second blade may be formed to have a predetermined width that is narrowest where the second blade is connected to the impeller.

これにより、第２の羽根の付け根から吸込口への液体の漏れによる圧力損失を防ぎ、液体の圧力を高めることができる。   Thereby, the pressure loss by the leakage of the liquid from the base of the 2nd blade | wing to a suction inlet can be prevented, and the pressure of a liquid can be raised.

さらに、前記ポンプケースは、吐出口内面の最上部を第２の羽根の上面より低い所定の高さに配置し吐出口内面の最下部を第２の羽根の下面より高い所定の高さに配置してもよい。   Further, in the pump case, the uppermost portion of the inner surface of the discharge port is disposed at a predetermined height lower than the upper surface of the second blade, and the lowermost portion of the inner surface of the discharge port is disposed at a predetermined height higher than the lower surface of the second blade. May be.

これにより、第２の羽根により高められた液体の圧力が分散することなく吐出口に伝えられ高圧力の液体を吐出するポンプを提供することができる。   As a result, it is possible to provide a pump that discharges a high-pressure liquid that is transmitted to the discharge port without the liquid pressure increased by the second blades being dispersed.

そして上記ポンプを電子部品の冷却装置等の液体供給装置に組み込むようにすれば、液体供給装置の使い勝手を大いに高めることができる。   If the pump is incorporated in a liquid supply apparatus such as a cooling device for electronic parts, the usability of the liquid supply apparatus can be greatly improved.

以下、本発明の実施例について図面を用いて説明する。   Embodiments of the present invention will be described below with reference to the drawings.

（実施例１）
図１の本発明の実施例１及び実施例２における電子部品の冷却装置の全体概要図に示すように、発熱部品１が基板２に実装されており、発熱部品１と冷媒とで熱交換を行ない発熱部品１を冷却する冷却器３が配置されている。 Example 1
As shown in the overall schematic diagram of the electronic component cooling apparatus in the first and second embodiments of the present invention shown in FIG. 1, the heat generating component 1 is mounted on the substrate 2, and heat exchange is performed between the heat generating component 1 and the refrigerant. A cooler 3 for cooling the heat generating component 1 is disposed.

また、冷媒から熱を取り除く放熱器４と、冷媒を貯めておくリザーブタンク５と、さらに冷媒を循環させるポンプ６が配置されていて、前記冷却器３と放熱器４とリザーブタンク５、及びポンプ６を接続する配管７が取りつけられている。   Further, a radiator 4 that removes heat from the refrigerant, a reserve tank 5 that stores the refrigerant, and a pump 6 that circulates the refrigerant are arranged. The cooler 3, the radiator 4, the reserve tank 5, and the pump A pipe 7 for connecting 6 is attached.

リザーブタンク５内の冷媒は、ポンプ６から吐出され、配管７を通って冷却器３に送られ、発熱部品１の熱を奪うことでその温度が上昇して放熱器４に送られ、放熱器４で冷されてその温度が降下してリザーブタンク５へ戻る。このように、ポンプ６で冷媒を循環させて発熱部品１を冷却するものである。   The refrigerant in the reserve tank 5 is discharged from the pump 6, sent to the cooler 3 through the pipe 7, deprived of heat of the heat generating component 1, and its temperature rises and is sent to the radiator 4. After being cooled at 4, the temperature drops and returns to the reserve tank 5. Thus, the heat generating component 1 is cooled by circulating the refrigerant by the pump 6.

また、図２（ａ）は本発明の実施例１及び実施例２における羽根車を透視して示すポンプの上面断面図、図２（ｂ）は本発明の実施例１及び実施例２における羽根車を透視して示すポンプの正面断面図、図３（ａ）は本発明の実施例１における羽根車を透視して示すポンプの上面断面図、図３（ｂ）は本発明の実施例１における羽根車を透視して示すポンプの正面断面図、図４（ａ）は本発明の実施例１における羽根車を透視して示すポンプの上面断面図、図４（ｂ）は本発明の実施例１における羽根車を透視して示すポンプの正面断面図を示すように、１２は冷媒が吸込まれる導入口となる吸込口、１３は冷媒が吐出される吐出口、１１はポンプケースであり吸込口１２と吐出口１３が接続されている。   2 (a) is a top sectional view of the pump shown through the impeller in the first and second embodiments of the present invention, and FIG. 2 (b) is a blade in the first and second embodiments of the present invention. FIG. 3A is a front sectional view of the pump seen through the car, FIG. 3A is a top sectional view of the pump seen through the impeller in the first embodiment of the present invention, and FIG. 3B is the first embodiment of the present invention. 4A is a front sectional view of the pump shown through the impeller in FIG. 4, FIG. 4A is a top sectional view of the pump shown through the impeller in Example 1 of the present invention, and FIG. As shown in the front cross-sectional view of the pump seen through the impeller in Example 1, 12 is a suction port that serves as an inlet through which refrigerant is sucked, 13 is a discharge port from which refrigerant is discharged, and 11 is a pump case. The suction port 12 and the discharge port 13 are connected.

１４は羽根車でありポンプケース１１に内蔵されている。１４ａは羽根車１４の中心より所定の距離から羽根車１４の外周に向かって所定の長さと厚みを持って取り付けられた第１の羽根であり、１４ｂは第１の羽根１４ａの外周部であり羽根車１４の側面部に所定の長さと高さをもって取り付けられた第２の羽根である。   Reference numeral 14 denotes an impeller which is built in the pump case 11. 14a is a first blade attached with a predetermined length and thickness from the center of the impeller 14 toward the outer periphery of the impeller 14, and 14b is an outer peripheral portion of the first blade 14a. It is the 2nd blade | wing attached to the side part of the impeller 14 with predetermined length and height.

１８は第１の羽根１４ａを吸込口１２側から覆うように取り付けられたシュラウドである。１５はポンプ部でありポンプケース１１と羽根車１４とにより液体に圧力エネルギーを与える部分である。１６はモータ部であり羽根車１４を駆動させる動力源である。１７は回転軸でありモータ部１６の回転力を羽根車１４に伝播する。   A shroud 18 is attached so as to cover the first blade 14a from the inlet 12 side. Reference numeral 15 denotes a pump portion which gives pressure energy to the liquid by the pump case 11 and the impeller 14. A motor unit 16 is a power source that drives the impeller 14. Reference numeral 17 denotes a rotation shaft that propagates the rotational force of the motor unit 16 to the impeller 14.

このような構成を持つポンプ及びそのポンプを備えた冷却装置について、以下、図１から図４を用いて説明する。   Hereinafter, a pump having such a configuration and a cooling device including the pump will be described with reference to FIGS.

図１及び図２においてポンプ６が駆動されると、羽根車１４の回転により羽根車１４の中心部は負圧となり、リザーブタンク５内の冷媒は吸込口１２から羽根車１４の中心部に導入される。   When the pump 6 is driven in FIGS. 1 and 2, the central portion of the impeller 14 becomes negative pressure due to the rotation of the impeller 14, and the refrigerant in the reserve tank 5 is introduced from the suction port 12 into the central portion of the impeller 14. Is done.

導入された冷媒は、羽根車１４の遠心力により第１の羽根１４ａに沿って加圧されながらポンプケース１１の内壁及び第２の羽根１４ｂへと導かれる。第２の羽根１４ｂに導かれた冷媒は第２の羽根１４ｂの裏側で剥離し渦を発生する。発生した渦は第２の羽根１４ｂの遠心力によりポンプケース１１の内壁にてさらに加圧されながら再度後段の第２の羽根１４ｂに戻り、渦を加速させる。   The introduced refrigerant is guided to the inner wall of the pump case 11 and the second blade 14 b while being pressurized along the first blade 14 a by the centrifugal force of the impeller 14. The refrigerant guided to the second blade 14b is separated from the back side of the second blade 14b to generate a vortex. The generated vortex returns to the second blade 14b in the subsequent stage while being further pressurized on the inner wall of the pump case 11 by the centrifugal force of the second blade 14b, and accelerates the vortex.

こうして吐出口１３に到達するまで繰返し加圧されて高圧の渦となった冷媒は、ポンプケース１１の内壁に沿いながら吐出口１３に誘導される。   The refrigerant that has been repeatedly pressurized until it reaches the discharge port 13 and becomes a high-pressure vortex is guided to the discharge port 13 along the inner wall of the pump case 11.

このとき図３に示すように第２の羽根１４ｂが羽根車１４の中心線に対して羽根車１４の回転方向と反対方向に所定の角度で傾斜させて配置すると、第２の羽根１４ｂの裏で発生した剥離による渦は第２の羽根１４ｂの回転方向側の面を転がりながらさらに回転を加速し、第２の羽根１４ｂの遠心力により容易に第２の羽根１４ｂから飛び出してポンプケース１１の内壁にてさらに加圧される。   At this time, as shown in FIG. 3, if the second blade 14b is disposed at a predetermined angle in the direction opposite to the rotation direction of the impeller 14 with respect to the center line of the impeller 14, the back of the second blade 14b is disposed. The vortex due to the separation generated in step 2 further accelerates the rotation while rolling the surface of the second blade 14b on the rotational direction side, and easily jumps out of the second blade 14b by the centrifugal force of the second blade 14b. Further pressure is applied to the inner wall.

そして、再度後段の第２の羽根１４ｂに戻り、渦を発生させるためさらに効果的に冷媒に運動エネルギーを与えることができる。   And it returns to the 2nd blade | wing 14b of a back | latter stage again, and since a vortex is generated, a kinetic energy can be given to a refrigerant | coolant more effectively.

第２の羽根１４ｂの羽根車１４の中心線に対する傾斜角度は２０°〜７０°、より好ましくは３５〜５５°、最も好ましいのは４５°である。   The inclination angle of the second blade 14b with respect to the center line of the impeller 14 is 20 ° to 70 °, more preferably 35 ° to 55 °, and most preferably 45 °.

また第２の羽根１４ｂの回転方向側の面はその形状が回転軸１７方向から見た場合に直線であるだけでなく、曲線を描いた凹形状であってもよい。   Further, the surface on the rotational direction side of the second blade 14b is not only a straight line when viewed from the direction of the rotational axis 17, but may be a concave shape having a curved line.

さらに図４に示すようにシュラウド１８により第１の羽根１４ａを吸込口１２側から覆うように取り付けることで、第１の羽根１４ａの遠心力により加圧された冷媒はポンプ部１５内で対流することなく確実に第２の羽根１４ｂに導かれる為さらに効率よく冷媒の圧力を高めることができる。   Further, as shown in FIG. 4, the first blade 14 a is attached by the shroud 18 so as to cover the suction port 12, so that the refrigerant pressurized by the centrifugal force of the first blade 14 a convects in the pump unit 15. Since it is reliably guided to the second blade 14b without any problem, the refrigerant pressure can be increased more efficiently.

ポンプ６が駆動され吐出口１３から高圧の冷媒が吐出されると、リザーブタンク５内の冷媒は、配管７を通って冷却器３に送られ、発熱部品１の熱を奪うことでその温度が上昇して放熱器４に送られ、放熱器４で冷されてその温度が降下してリザーブタンク５へ戻る。   When the pump 6 is driven and high-pressure refrigerant is discharged from the discharge port 13, the refrigerant in the reserve tank 5 is sent to the cooler 3 through the pipe 7, and the temperature of the refrigerant is reduced by taking the heat of the heat generating component 1. The temperature rises and is sent to the radiator 4, is cooled by the radiator 4, drops in temperature, and returns to the reserve tank 5.

このように、ポンプ６で冷媒を循環させて発熱部品１を冷却するものである。冷却器３やリザーブタンク５内の流路は冷却器３においては受熱性能を高めるため、リザーブタンク５においては冷媒中の気泡を分離するための気液分離を行うために特に配管抵抗が高くなっている。   Thus, the heat generating component 1 is cooled by circulating the refrigerant by the pump 6. The flow path in the cooler 3 and the reserve tank 5 increases the heat receiving performance in the cooler 3, and in the reserve tank 5, the pipe resistance is particularly high in order to perform gas-liquid separation for separating bubbles in the refrigerant. ing.

以上のように本実施例１によれば、羽根車１４の中心部から吸入した冷媒を第１の羽根１４ａによる遠心力で圧力を高めながら第２の羽根１４ｂまで導き、第２の羽根１４ｂとポンプケース１１との摩擦流によりさらに圧力を高めるのでモータ部１６の回転数を高めずとも羽根車１４内の高圧力の冷媒を羽根車１４の外周部にある吐出口１３から効率良く吐出させることができる。   As described above, according to the first embodiment, the refrigerant sucked from the central portion of the impeller 14 is guided to the second blade 14b while increasing the pressure by the centrifugal force of the first blade 14a, and the second blade 14b Since the pressure is further increased by the frictional flow with the pump case 11, the high-pressure refrigerant in the impeller 14 can be efficiently discharged from the discharge port 13 in the outer peripheral portion of the impeller 14 without increasing the rotational speed of the motor unit 16. Can do.

また回転軸１７を支える摺動部の長寿命化も図れる。   In addition, the life of the sliding portion that supports the rotating shaft 17 can be extended.

なお、上記ポンプはモータ部１６と羽根車１４とを回転軸１７にて連結させる構成としたが、羽根車１４にマグネットを取り付け、ポンプケース１１に固定された軸の周りを羽根車１４が回転するアウターローター型のモータによるポンプにても同様に摺動部の寿命を延ばすことができる。   In addition, although the said pump was set as the structure which connected the motor part 16 and the impeller 14 with the rotating shaft 17, a magnet is attached to the impeller 14 and the impeller 14 rotates around the axis | shaft fixed to the pump case 11. Similarly, the life of the sliding portion can be extended even in a pump using an outer rotor type motor.

（実施例２）
図１に示すように、発熱部品１が基板２に実装されており、発熱部品１と冷媒とで熱交換を行ない発熱部品１を冷却する冷却器３が配置されている。 (Example 2)
As shown in FIG. 1, a heat generating component 1 is mounted on a substrate 2, and a cooler 3 that performs heat exchange between the heat generating component 1 and a refrigerant to cool the heat generating component 1 is disposed.

また、冷媒から熱を取り除く放熱器４と、冷媒を貯めておくリザーブタンク５と、さらに冷媒を循環させるポンプ６が配置されていて、前記冷却器３と放熱器４とリザーブタンク５、及びポンプ６を接続する配管７が取りつけられている。   Further, a radiator 4 that removes heat from the refrigerant, a reserve tank 5 that stores the refrigerant, and a pump 6 that circulates the refrigerant are arranged. The cooler 3, the radiator 4, the reserve tank 5, and the pump A pipe 7 for connecting 6 is attached.

リザーブタンク５内の冷媒は、ポンプ６から吐出され、配管７を通って冷却器３に送られ、発熱部品１の熱を奪うことでその温度が上昇して放熱器４に送られ、放熱器４で冷されてその温度が降下してリザーブタンク５へ戻る。このように、ポンプ６で冷媒を循環させて発熱部品１を冷却するものである。   The refrigerant in the reserve tank 5 is discharged from the pump 6, sent to the cooler 3 through the pipe 7, deprived of heat of the heat generating component 1, and its temperature rises and is sent to the radiator 4. After being cooled at 4, the temperature drops and returns to the reserve tank 5. Thus, the heat generating component 1 is cooled by circulating the refrigerant by the pump 6.

また図２に示すように、１２は冷媒が吸込まれる導入口となる吸込口、１３は冷媒が吐出される吐出口、１１はポンプケースであり吸込口１２と吐出口１３が接続されている。１４は羽根車でありポンプケース１１に内蔵されている。   As shown in FIG. 2, 12 is a suction port that serves as an inlet for sucking refrigerant, 13 is a discharge port from which refrigerant is discharged, 11 is a pump case, and the suction port 12 and the discharge port 13 are connected. . Reference numeral 14 denotes an impeller which is built in the pump case 11.

１４ａは羽根車１４の中心より所定の距離から羽根車１４の外周に向かって所定の長さと厚みを持って取り付けられた第１の羽根であり、１４ｂは第１の羽根１４ａの外周部であり羽根車１４の側面部に所定の長さと高さをもって取り付けられた第２の羽根である。   14a is a first blade attached with a predetermined length and thickness from the center of the impeller 14 toward the outer periphery of the impeller 14, and 14b is an outer peripheral portion of the first blade 14a. It is the 2nd blade | wing attached to the side part of the impeller 14 with predetermined length and height.

ポンプケース１１の内面と第２の羽根１４ｂとの間隙は、第２の羽根１４ｂが第１の羽根１４ａに接続されている部分が最も狭くなっている。吐出口１３の内面の最上部は第２の羽根１４ｂの上面より低い所定の高さに配置され、吐出口１３の内面の最下部は第２の羽根１４ｂの下面より高い所定の高さに配置されている。   The gap between the inner surface of the pump case 11 and the second blade 14b is narrowest at the portion where the second blade 14b is connected to the first blade 14a. The uppermost portion of the inner surface of the discharge port 13 is disposed at a predetermined height lower than the upper surface of the second blade 14b, and the lowermost portion of the inner surface of the discharge port 13 is disposed at a predetermined height higher than the lower surface of the second blade 14b. Has been.

１５はポンプ部でありポンプケース１１と羽根車１４とにより液体に圧力エネルギーを与える部分である。１６はモータ部であり羽根車１４を駆動させる動力源である。１７は回転軸でありモータ部１６の回転力を羽根車１４に伝播する。   Reference numeral 15 denotes a pump portion which gives pressure energy to the liquid by the pump case 11 and the impeller 14. A motor unit 16 is a power source that drives the impeller 14. Reference numeral 17 denotes a rotation shaft that propagates the rotational force of the motor unit 16 to the impeller 14.

このような構成を持つポンプ６及びそのポンプ６を備えた冷却装置について、以下図１及び図２を用いて説明する。   The pump 6 having such a configuration and the cooling device including the pump 6 will be described below with reference to FIGS. 1 and 2.

図１及び図２においてポンプ６が駆動されると、羽根車１４の回転により羽根車１４の中心部は負圧となり、リザーブタンク５内の冷媒は吸込口１２から羽根車１４の中心部に導入される。   When the pump 6 is driven in FIGS. 1 and 2, the central portion of the impeller 14 becomes negative pressure due to the rotation of the impeller 14, and the refrigerant in the reserve tank 5 is introduced from the suction port 12 into the central portion of the impeller 14. Is done.

導入された冷媒は、羽根車１４の遠心力により第１の羽根１４ａに沿って加圧されながらポンプケース１１の内壁及び第２の羽根１４ｂへと導かれる。第２の羽根１４ｂに導かれた冷媒は第２の羽根１４ｂの裏側で剥離し渦を発生する。   The introduced refrigerant is guided to the inner wall of the pump case 11 and the second blade 14 b while being pressurized along the first blade 14 a by the centrifugal force of the impeller 14. The refrigerant guided to the second blade 14b is separated from the back side of the second blade 14b to generate a vortex.

第２の羽根１４ｂとポンプケース１１の内面との間には間隙があり、第２の羽根１４ｂとポンプケース１１の内面との間隙は、第２の羽根１４ｂが第１の羽根１４ａに接続されている部分が最も狭くなっているため、冷媒は第２の羽根１４ｂに対して羽根車１４の外周方向だけでなく第２の羽根１４ｂの上面端にても剥離して渦を発生する。   There is a gap between the second blade 14b and the inner surface of the pump case 11, and the gap between the second blade 14b and the inner surface of the pump case 11 is such that the second blade 14b is connected to the first blade 14a. Therefore, the refrigerant separates from the second blade 14b not only in the outer circumferential direction of the impeller 14 but also at the upper surface end of the second blade 14b to generate a vortex.

発生した渦は第２の羽根１４ｂの遠心力によりポンプケース１１の内壁にてさらに加圧されながら再度後段の第２の羽根１４ｂに戻り、渦を加速させる。こうして吐出口１３に到達するまで繰返し加圧されて高圧の渦となった冷媒は、ポンプケース１１の内壁に沿いながら吐出口１３に誘導される。   The generated vortex returns to the second blade 14b in the subsequent stage while being further pressurized on the inner wall of the pump case 11 by the centrifugal force of the second blade 14b, and accelerates the vortex. The refrigerant that has been repeatedly pressurized until it reaches the discharge port 13 and becomes a high-pressure vortex is guided to the discharge port 13 along the inner wall of the pump case 11.

第２の羽根１４ｂとポンプケース１１の内面との間隙は、第２の羽根１４ｂが第１の羽根１４ａに接続されている部分が最も狭くなっているため、羽根車１４の外周部分で圧力を高めた冷媒が、圧力が低い吸込口１２側へと逆流するのを防止し、よって冷媒の圧力低下を防ぐ。   The gap between the second blade 14b and the inner surface of the pump case 11 is narrowest at the portion where the second blade 14b is connected to the first blade 14a. The increased refrigerant is prevented from flowing back to the suction port 12 side where the pressure is low, and thus the pressure drop of the refrigerant is prevented.

ポンプケース１１の内面と第２の羽根１４ｂの付け根の部分の間隙は１．５ｍｍ以下であればよいが好ましくは０．５ｍｍ以下であり最適は０．１ｍｍ程度である。   The gap between the inner surface of the pump case 11 and the base of the second blade 14b may be 1.5 mm or less, preferably 0.5 mm or less, and optimally about 0.1 mm.

さらに吐出口１３の内面の最上部は第２の羽根１４ｂの上面より低い所定の高さに配置され、吐出口１３の内面の最下部は第２の羽根１４ｂの下面より高い所定の高さに配置されているため、羽根車１４の外周部にて第２の羽根１４ｂにより高圧となった冷媒が吐出口１３の入り口で拡散して圧力が程化するのを防ぐ。   Further, the uppermost part of the inner surface of the discharge port 13 is arranged at a predetermined height lower than the upper surface of the second blade 14b, and the lowermost part of the inner surface of the discharge port 13 is set at a predetermined height higher than the lower surface of the second blade 14b. Therefore, the refrigerant whose pressure has been increased by the second blade 14 b at the outer peripheral portion of the impeller 14 is prevented from diffusing at the entrance of the discharge port 13 to reduce the pressure.

吐出口１３の入り口部は第２の羽根１４ｂの下面から上面の範囲以内にあればよいが、好ましくは吐出口１３の入り口部高さは第２の羽根１４ｂの高さに対して比率にして１以下、好ましくは０．８以下であり、最適値は０．７以下である。   The inlet portion of the discharge port 13 may be within the range from the lower surface to the upper surface of the second blade 14b. Preferably, the height of the inlet portion of the discharge port 13 is a ratio to the height of the second blade 14b. 1 or less, preferably 0.8 or less, and the optimum value is 0.7 or less.

ポンプ６が駆動され吐出口１３から高圧の冷媒が吐出されると、リザーブタンク５内の冷媒は、配管７を通って冷却器３に送られ、発熱部品１の熱を奪うことでその温度が上昇して放熱器４に送られ、放熱器４で冷されてその温度が降下してリザーブタンク５へ戻る。   When the pump 6 is driven and high-pressure refrigerant is discharged from the discharge port 13, the refrigerant in the reserve tank 5 is sent to the cooler 3 through the pipe 7, and the temperature of the refrigerant is reduced by taking the heat of the heat generating component 1. The temperature rises and is sent to the radiator 4, is cooled by the radiator 4, drops in temperature, and returns to the reserve tank 5.

このように、ポンプ６で冷媒を循環させて発熱部品１を冷却するものである。冷却器３やリザーブタンク５内の流路は冷却器３においては受熱性能を高めるため、リザーブタンク５においては冷媒中の気泡を分離するための気液分離を行うために特に配管抵抗が高くなっている。   Thus, the heat generating component 1 is cooled by circulating the refrigerant by the pump 6. The flow path in the cooler 3 and the reserve tank 5 increases the heat receiving performance in the cooler 3, and in the reserve tank 5, the pipe resistance is particularly high in order to perform gas-liquid separation for separating bubbles in the refrigerant. ing.

以上のように本実施例２によれば、羽根車１４中心部から吸入した冷媒を第１の羽根１４ａによる遠心力で圧力を高めながら第２の羽根１４ｂまで導き、第２の羽根１４ｂとポンプケース１１との摩擦流によりさらに圧力を高め、圧力の高まった冷媒が吸込口１２へ逆流することを防止し、また吐出口１３の入り口で冷媒の圧力が分散することを防ぐため、モータ部１６の回転数を高めずとも羽根車１４内の高圧力の冷媒を羽根車１４の外周部にある吐出口１３から効率良く吐出させることができる。   As described above, according to the second embodiment, the refrigerant sucked from the central part of the impeller 14 is guided to the second blade 14b while increasing the pressure by the centrifugal force of the first blade 14a, and the second blade 14b and the pump In order to further increase the pressure by the frictional flow with the case 11, to prevent the refrigerant having increased pressure from flowing back to the suction port 12 and to prevent the refrigerant pressure from being dispersed at the inlet of the discharge port 13, the motor unit 16. The high-pressure refrigerant in the impeller 14 can be efficiently discharged from the discharge port 13 in the outer peripheral portion of the impeller 14 without increasing the rotational speed of the impeller 14.

また回転軸１７を支える摺動部の長寿命化も図れる。   In addition, the life of the sliding portion that supports the rotating shaft 17 can be extended.

なお、上記ポンプはモータ部１６と羽根車１４とを回転軸１７にて連結させる構成としたが、羽根車１４にマグネットを取り付け、ポンプケース１１に固定された軸の周りを羽根車１４が回転するアウターローター型のモータによるポンプでも同様に摺動部の寿命を延ばすことができる。   In addition, although the said pump was set as the structure which connected the motor part 16 and the impeller 14 with the rotating shaft 17, a magnet is attached to the impeller 14 and the impeller 14 rotates around the axis | shaft fixed to the pump case 11. Similarly, a pump using an outer rotor type motor can extend the life of the sliding portion.

本発明の液体供給装置は、例えば燃料電池装置やヒートポンプ装置等に使用される様々な液体供給装置への応用が期待できる。   The liquid supply device of the present invention can be expected to be applied to various liquid supply devices used in, for example, fuel cell devices and heat pump devices.

本発明の実施例１及び実施例２における電子部品の冷却装置の全体概要図1 is an overall schematic diagram of an electronic component cooling device according to Embodiment 1 and Embodiment 2 of the present invention （ａ）本発明の実施例１及び実施例２における羽根車を透視して示すポンプの上面断面図、（ｂ）本発明の実施例１及び実施例２における羽根車を透視して示すポンプの正面断面図(A) Top sectional view of the pump shown through the impeller in Example 1 and Example 2 of the present invention, (b) Pump of the pump shown through through the impeller in Example 1 and Example 2 of the present invention Front sectional view （ａ）本発明の実施例１における羽根車を透視して示すポンプの上面断面図、（ｂ）本発明の実施例１における羽根車を透視して示すポンプの正面断面図(A) Top sectional view of the pump shown through the impeller in Example 1 of the present invention, (b) Front sectional view of the pump shown through the impeller in Example 1 of the present invention （ａ）本発明の実施例１における羽根車を透視して示すポンプの上面断面図、（ｂ）本発明の実施例１における羽根車を透視して示すポンプの正面断面図(A) Top sectional view of the pump shown through the impeller in Example 1 of the present invention, (b) Front sectional view of the pump shown through the impeller in Example 1 of the present invention

符号の説明Explanation of symbols

１ 発熱部品
２ 基板
３ 冷却器
４ 放熱器
５ リザーブタンク
６ ポンプ
７ 配管
１１ ポンプケース
１２ 吸込口
１３ 吐出口
１４ 羽根車
１４ａ 第１の羽根
１４ｂ 第２の羽根
１５ ポンプ部
１６ モータ部
１７ 回転軸
１８ シュラウド DESCRIPTION OF SYMBOLS 1 Heat generating component 2 Board | substrate 3 Cooler 4 Radiator 5 Reserve tank 6 Pump 7 Piping 11 Pump case 12 Suction port 13 Discharge port 14 Impeller 14a 1st blade | wing 14b 2nd blade | wing 15 Pump part 16 Motor part 17 Rotating shaft 18 Shroud

Claims (5)

液体を吸排する羽根車を内蔵したポンプ部と、液体を吸入する吸入口と液体を吐出する吐出口が接続されポンプ部を収納するポンプケースと、羽根車を駆動するモータ部とを有し、前記羽根車は、前記吸入口からの液体が前記羽根車の中心に導入されると共に、前記中心より外周に向かって放射状に形成された第１の羽根を備え、前記第１の羽根の外周部であって羽根車の側面部に第２の羽根を設け、前記第２の羽根の外周に吐出口を設けると共に、前記吐出口はポンプケースの内側に開口した入り口部の内面の最上部と最下部の間の回転軸方向に沿った高さ寸法が第２の羽根の上面と下面の間の高さ寸法より小さく、かつ吐出口内面の最上部を第２の羽根の上面より低い位置に配置し吐出口内面の最下部を第２の羽根の下面より高い位置に配置したことを特徴とするポンプ。 Has a pump unit with a built-impeller suction and discharge of liquid, and a pump casing the discharge port for accommodating the connected pump unit for discharging an inlet and a liquid inhaling liquids, and a motor unit for driving the impeller The impeller includes a first blade that is introduced from the suction port into the center of the impeller and that is radially formed from the center toward the outer periphery, and the outer periphery of the first blade. a part of the second blade provided on the side portion of the impeller, provided with a discharge opening on the outer periphery of the second blade, the discharge port and the top of the inner surface of the inlet portion which is open to the inside of the pump case The height dimension along the rotation axis direction between the lowermost portions is smaller than the height dimension between the upper surface and the lower surface of the second blade, and the uppermost portion of the inner surface of the discharge port is lower than the upper surface of the second blade. Place the lowermost part of the inner surface of the discharge port higher than the lower surface of the second blade Pump, characterized in that the location. 前記第２の羽根は、羽根車の中心線に対して羽根車の回転方向と反対側に傾斜して配置したことを特徴とする請求項１記載のポンプ。 It said second blade includes a pump according to claim 1, characterized in that arranged inclined obliquely on the side opposite to the rotational direction of the impeller with respect to the center line of the impeller. 前記第１の羽根の吸入口側に第１の羽根を覆う覆板を配置したことを特徴とする請求項１または２記載のポンプ。 3. The pump according to claim 1, wherein a cover plate that covers the first blade is disposed on the suction port side of the first blade. 前記ポンプケースの内面と前記第２の羽根との間に間隙を有し、前記間隙を前記第２の羽根の付け根の位置で最も狭くしたことを特徴とする請求項１から３のいずれか１項に記載のポンプ。 The gap between the inner surface of the pump case and the second blade has a gap, and the gap is narrowest at the base of the second blade. The pump according to item. 請求項１〜４のいずれか１項に記載のポンプを備えた液体供給装置。The liquid supply apparatus provided with the pump of any one of Claims 1-4.
JP2005066994A 2005-03-10 2005-03-10 Pump and liquid supply apparatus having the same Expired - Fee Related JP4770207B2 (en)

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JP4770207B2 true JP4770207B2 (en) 2011-09-14

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JP7234041B2 (en) * 2019-05-31 2023-03-07 三菱重工業株式会社 impeller and centrifugal pump

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JPS4913702A (en) * 1972-05-17 1974-02-06
JPS57188996A (en) * 1981-05-18 1982-11-20 Matsushita Electric Ind Co Ltd Device for heat emission
JPS63100296A (en) * 1986-10-15 1988-05-02 Nippon Denso Co Ltd Fuel pump
JPH0354392A (en) * 1989-07-20 1991-03-08 Jidosha Denki Kogyo Co Ltd Miniature pump for automobile
JPH05248385A (en) * 1992-03-10 1993-09-24 Taiheiyo Kiko Kk Swirl impeller
JP3313061B2 (en) * 1998-01-29 2002-08-12 日機装株式会社 Centrifugal pump
JP3730601B2 (en) * 2002-07-11 2006-01-05 日機装株式会社 Self-priming vortex pump
JP2004183630A (en) * 2002-12-06 2004-07-02 Mitsubishi Heavy Ind Ltd Vortex pump

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