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

Description

  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.

  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.

  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.

  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.

  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.

  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).

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

  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.

  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. .

  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.

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.

  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.

  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.

  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.

  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.

  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.

  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.

  A cover plate that covers the first blade may be disposed on the suction port side of the first blade.

  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.

  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.

  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.

  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.

  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.

  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.

  Embodiments of the present invention will be described below with reference to the drawings.

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.

  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.

  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.

  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.

  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.

  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.

  Hereinafter, a pump having such a configuration and a cooling device including the pump will be described with reference to FIGS.

  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.

  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.

  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.

  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.

  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.

  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 °.

  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.

  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.

  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.

  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.

  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.

  In addition, the life of the sliding portion that supports the rotating shaft 17 can be extended.

  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.

(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.

  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.

  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.

  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 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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  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.

  In addition, the life of the sliding portion that supports the rotating shaft 17 can be extended.

  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.

  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.

1 is an overall schematic diagram of an electronic component cooling device according to Embodiment 1 and Embodiment 2 of the present invention (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) 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) 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

Explanation of symbols

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)

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. 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. 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. 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. The liquid supply apparatus provided with the pump of any one of Claims 1-4.

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