JP2014145269A - Vehicular pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a vehicular pump device capable of improving pump efficiency by suppressing pressure loss in a pump without deteriorating strength of an impeller.SOLUTION: An electric pump 12 comprises a pump case 16 which has an inlet pipe 30, an outlet pipe 32, and a swirl chamber 37. The electric pump 12 further comprises an impeller 18. The impeller 18 comprises a first disc part 78, a second disc part 80 having an opening 102, and blades 82 provided to stand between the first disc part 78 and the second disc part 80. An inner diameter D1 of the opening 102 is set at 16 mm, an inlet angle β1 of the blades 82 is set at 35 degrees, an outlet angle β2 of the blades 82 is set at 18 degrees, and (a distance b2 between an outer peripheral end 106 of the first disc part 78 and an outer peripheral end 108 of the second disc part 80)/(a distance b1 between an inner peripheral edge 102A of the opening 102 and the first disc part 78) is set at 0.7.

Description

  The present invention relates to a vehicle pump device.

  Conventionally, when the difference between the flow angle of the working fluid at the inlet of the impeller and the inlet angle of the impeller becomes large, the circumferential direction of the working fluid (circumferential direction of the impeller) when the working fluid flows into the inlet of the impeller It is known that the pressure loss increases as the speed decreases or is accelerated. In order to solve the problem, the following Non-Patent Document 1 describes that the pressure loss is suppressed by sharpening the tip of the inlet of the impeller.

  Moreover, in the design of the conventional centrifugal pump, as described in Non-Patent Document 1 and Non-Patent Document 2 below, specifications of the impeller and the spiral chamber are determined based on experimentally obtained design constants. The

Masayoshi Omachi, “Design of Spiral Pump”, 7th Edition, Power Company, April 20, 1993, p. 61 A. J. et al. Stepanoff "centrifugal pump and axial pump" Maruzen

  However, in the configuration described in Non-Patent Document 1, pressure loss is reduced as the tip of the impeller is sharpened (as the tip of the impeller becomes sharper), but as the tip of the impeller is sharpened. The strength of the impeller inlet (tip of the impeller) decreases.

  Further, in a pump that is required to be downsized in the radial direction, such as a vehicle pump device, it is difficult to secure a sufficient area of the spiral chamber, and as a result, it is difficult to obtain high pump efficiency.

  An object of the present invention is to obtain a vehicular pump device capable of suppressing the pressure loss in the pump and improving the pump efficiency without lowering the strength of the impeller in consideration of the above facts.

  According to a first aspect of the present invention, there is provided a vehicular pump device according to the present invention. A pump case having an outflow portion, and a spiral chamber gradually expanding in the circumferential direction; the pump case rotatably supported in the pump case; and a first disc portion formed in a disc shape; A second disk part disposed opposite the one disk part and formed in a disk shape and having a circular opening in the axial center part; and standing between the first disk part and the second disk part And a vane extending radially outward of the first disk portion and the second disk portion, and pumping the working fluid from the inflow portion toward the outflow portion by rotating around an axis. A flow rate of 10 to 30 L / in, the discharge pressure is 30 to 80 kPa, and the specific speed (m, m3 / min, min-1) is 100 to 300, the maximum radius of the spiral chamber is 35 mm or less, and the inner diameter of the opening is 14 to 20 mm, the inlet angle of the blades is set to a range of 30 to 40 deg, the outlet angle of the blades is set to 22 deg or less, and (the outer peripheral edge of the first disk part and the outer peripheral edge of the second disk part) The distance b2) / (distance b1 between the inner peripheral edge portion of the opening and the first disk portion) is in the range of 0.6 to 0.8.

In the present invention according to claim 1, the flow rate is 10 to 30 L / min, the discharge pressure is 30 to 80 kPa, and the specific speed (m, m ³ / min, min ⁻¹ ) is operated in the range of 100 to 300. The pressure loss in the pump can be suppressed and the pump efficiency can be improved without reducing the strength of the impeller of the vehicular pump device whose maximum radius is 35 mm or less. That is, in this invention, while the internal diameter of the opening part formed in the 2nd disk part which comprises a part of impeller is 14-20 mm, the inlet angle of the blade | wing which comprises the other part of an impeller Is in the range of 30 to 40 deg. Therefore, the difference between the flow angle of the working fluid at the inlet of the impeller (the inner peripheral end of the blade) and the inlet angle of the blade (the angle of the inner peripheral end of the blade) is reduced. Thereby, in this invention, the pressure loss of the working fluid in the inlet_port | entrance of a blade | wing can be suppressed, without reducing the wall thickness of the inner peripheral edge part of a blade | wing. In the present invention, the exit angle of the blade is set to 22 deg or less, and (distance b2 between the outer peripheral edge of the first disk part and the outer peripheral edge of the second disk part) / (the inner peripheral edge part of the opening part and the first The value of the distance b1) with respect to the one disc part is in the range of 0.5 to 0.8. Therefore, the radial component of the flow velocity of the working fluid flowing out from the outlet of the impeller (blade outer peripheral end) is reduced, and the vortex generated in the spiral chamber is weakened, so that the pressure loss generated in the spiral chamber is suppressed. It comes out.

  A vehicle pump device according to a second aspect of the present invention is the vehicle pump device according to the first aspect, wherein the opening has an inner diameter of 16 to 18 mm and an inlet angle of the blades of 35 degrees or more. .

  In the second aspect of the present invention, the inner diameter of the opening and the inlet angle of the blade are set in the above ranges. Therefore, the difference between the working fluid flow angle at the impeller inlet (blade inner peripheral end) and the blade inlet angle (blade inner peripheral end angle) is further reduced. The pressure loss of the working fluid at the inlet can be further suppressed. That is, in the present invention, the pump efficiency can be further improved.

It is sectional drawing which shows the electric pump of this embodiment. It is sectional drawing which shows the cross section of the pump case which forms the outline of a pump part. It is sectional drawing which shows the cross section of a motor housing. It is a longitudinal cross-sectional view which shows the cross section which cut | disconnected the impeller along the axial direction. It is a plane sectional view showing a section of an impeller cut along line 4B-4B shown in FIG. 4A. It is an expanded sectional view expanding and showing the end part of the diameter direction inner side of the blade of the impeller shown in Drawing 4B. It is an expanded sectional view expanding and showing the end part of the diameter direction outside of the blade of the impeller shown in Drawing 4B. It is a plane sectional view showing a spiral chamber and an impeller in a section cut along line 6-6 in FIG. 1A. It is a graph which shows the relationship between the inlet angle of a blade | wing, pump efficiency, and discharge pressure. It is the schematic diagram which showed typically the mode of the flow of the working fluid which flows in into a spiral chamber from an impeller when the electric pump of this embodiment act | operates. It is the schematic diagram which showed typically distribution of the vorticity of the pump chamber when the electric pump of this embodiment act | operates. It is a graph which shows the relationship between the exit angle of a blade | wing, pump efficiency, and discharge pressure. It is a graph which shows the relationship between b2 / b1 of an impeller, pump efficiency, and discharge pressure. It is a graph which shows the relationship between the internal diameter of the opening part formed in the 2nd disk part, pump efficiency, and discharge pressure. It is the schematic diagram which showed typically the mode of the flow of the working fluid which flows in into a spiral chamber from an impeller when the electric pump which concerns on a proportional operation act | operates. It is the schematic diagram which showed typically distribution of the vorticity of the pump chamber when the electric pump which concerns on a proportionality act | operates.

  Next, the electric pump according to the embodiment of the present invention will be described.

As shown in FIG. 1, an electric pump 12 as a vehicle pump device of the present embodiment is a water pump for pumping cooling water into an inverter mounted on a hybrid vehicle or the like, and has a flow rate of 10 to 10. The operation is performed in a range of 30 L / min, a discharge pressure of 30 to 80 kPa, and a specific speed of 100 to 300 m, m ³ / min, min ⁻¹ . Specifically, the electric pump 12 includes a pump case 16 that forms an outline of the pump unit 14 that pumps in flowing cooling water, and a rotor 20 that drives the pump unit 14 by rotating an impeller 18 as an impeller. It is equipped with. In addition, the electric pump 12 includes a stator 22 that rotates the rotor 20 around the axis line by a magnetic field that the motor pump 12 generates, and a motor housing 24 that supports the stator 22. The motor unit 10 is configured with the rotor 20 and the stator 22 as main elements. Furthermore, the electric pump 12 includes a circuit device 28 for controlling the motor unit 10.

  Hereinafter, the configuration of the pump case 16, the motor housing 24, the rotor 20, the stator 22, and the circuit device 28 will be described first, and then the configuration of the impeller 18 will be described.

(Configuration of pump case 16)
As shown in FIG. 2, the pump case 16 includes an inlet pipe 30 as an inflow part into which cooling water (working fluid) flows and an outlet pipe 32 (see FIG. 6) as an outflow part from which cooling water flows out. It is an integrally molded product formed in a substantially cochlear shape. Specifically, the pump case 16 includes a substantially disk-plate-like base portion 34 and a bulging portion 36 that protrudes from the radially inner end of the base portion 34 to one side in the axial direction of the motor (in the direction of arrow A1). . As shown in FIGS. 2 and 6, a spiral chamber 37 that gradually increases in diameter along the circumferential direction is formed inside the bulging portion 36, and the maximum radius R of the spiral chamber 37 (the impeller 18 The distance from the axial center to the bulging portion is 32 mm.

  As shown in FIG. 2, the pump case 16 includes an impeller guide that extends from a radially inner end of the bulging portion 36 along a second disk portion 80 (see FIG. 4) of the impeller 18 described later. A portion 38 is provided. Furthermore, the pump case 16 includes a tubular inlet pipe 30 formed so as to extend from the radially inner end of the impeller guide portion 38 to one side in the axial direction of the motor (in the direction of arrow A1). Further, at the end of the inlet pipe 30, a retaining protrusion 30 </ b> A that suppresses the withdrawal of piping such as a rubber hose is formed. Further, the pump case 16 includes a tubular outlet pipe 32 that is connected to the bulging portion 36 and that extends in a direction perpendicular to the opening direction of the inlet pipe 30.

  Further, the pump case 16 includes a cylindrical open end 40 that extends from the radially outer end of the base 34 to the other axial side of the motor (in the direction of arrow A2).

  As shown in FIG. 1, an impeller 18 described later is accommodated in the pump case 16 described above, thereby forming a pump unit 14 that pumps cooling water flowing in from the inlet pipe 30 toward the outlet pipe 32. Yes.

(Configuration of motor housing 24)
As shown in FIG. 3, the motor housing 24 is an integrally molded product formed in a bottomed cylindrical shape. Specifically, a can portion 42 for accommodating a rotor 20 (see FIG. 4), which will be described later, is formed on one side of the motor housing 24 in the axial direction of the motor (in the direction of arrow A1). A stator accommodating portion 44 for accommodating a stator 22 (see FIG. 1) described later is formed on the other axial side of the motor (in the direction of arrow A2).

  The can portion 42 has a substantially U-shaped cross section that opens to one side of the motor in the axial direction (arrow A1 direction), and includes a circular bottom wall 46. In addition, a tubular shaft support portion 48 is provided at the center portion of the bottom wall 46 so as to protrude to one side in the axial direction of the motor (in the direction of arrow A1). The rotor 20 to be described later is supported by the shaft support portion 48, so that the rotor 20 can rotate about the shaft support portion 48 as an axis center. Further, the surface of the bottom wall 46 opposite to the surface on which the shaft support portion 48 is provided is an attachment surface 46A to which a circuit board 88 described later is attached. The mounting surface 46A is directed to the other side in the axial direction of the motor (in the direction of arrow A2) and extends in substantially the same direction as the circuit board 88 in a state where the circuit device 28 is mounted to the motor housing 24. doing.

  Further, the can part 42 includes an inner peripheral wall 50 that extends from the radially outer end of the bottom wall 46 to one side in the axial direction of the motor (in the direction of arrow A1). Further, the can part 42 includes a first impeller guide wall 52A extending from the end of the inner peripheral wall 50 to the radially outer side of the inner peripheral wall 50, and one end in the axial direction of the motor from the end of the first impeller guide wall 52A. A second impeller guide wall 52B extending in the direction of arrow A1 is provided. The first impeller guide wall 52A and the second impeller guide wall 52B are formed along an outer peripheral end portion of a first disk portion 78 of the impeller 18, which will be described later. The can 42 is formed by the bottom wall 46, the inner peripheral wall 50, the first impeller guide wall 52A, and the second impeller guide wall 52B described above.

  In addition, the motor housing 24 includes a side wall 54 that extends radially outward from the end of the second impeller guide wall 52 </ b> B of the can portion 42. Furthermore, the motor housing 24 includes a joining wall portion 56 that extends from the radially outer end of the side wall 54 to the other axial side of the motor (in the direction of arrow A2). As shown in FIG. 1, after this joining wall portion 56 and the open end portion 40 of the pump case 16 are fitted in the motor axial direction (arrow A1 and arrow A2 directions), heat welding or the like is performed. Are joined together.

  As shown in FIG. 3, the stator accommodating portion 44 has a W-shaped cross section that opens in the opposite direction to the can portion 42, and includes an annular bottom wall 58. The stator accommodating portion 44 includes an inner peripheral wall 50 that extends from the radially inner end of the bottom wall 58 toward the other axial side of the motor (in the direction of arrow A2). Furthermore, the stator housing portion 44 includes an outer peripheral wall 60 that extends from the radially outer end of the bottom wall 58 to the other axial side of the motor (in the direction of arrow A2). The stator housing portion 44 is formed by the bottom wall 58, the inner peripheral wall 50, and the outer peripheral wall 60 described above, and a stator 22 (described later) is surrounded by the bottom wall 58, the inner peripheral wall 50, and the outer peripheral wall 60. 1) is supported.

  Further, as shown in FIGS. 1 and 3, the motor housing 24 includes a connector portion 68 formed so as to protrude outward in the radial direction of the outer peripheral wall 60. The circuit device 28 is connected to a power source or the like via the connector portion 68.

(Configuration of rotor 20)
As shown in FIG. 1, the rotor 20 is configured by attaching a plurality of magnets 70 arranged in an annular shape to an output shaft 72. Specifically, the output shaft 72 is configured by subjecting a cylindrical steel material to surface treatment such as carburizing treatment, and one end thereof is a shaft support portion 48 (see FIG. 3) of the motor housing 24. ) To be inserted into the rotary shaft portion 72A. That is, the output shaft 72 is cantilevered by the shaft support 48.

  The magnet 70 is fixed to the output shaft 72 via a thick cylindrical support member 76 disposed on the outer side in the radial direction of the output shaft 72.

  An impeller 18 which will be described in detail later is attached to the end of the output shaft 72 opposite to the rotating shaft 72A.

(Configuration of stator 22)
As shown in FIGS. 1 and 3, the stator 22 includes a motor core 84 formed in an annular shape and a conductive winding 26 as main elements. Specifically, the motor core 84 is configured by laminating steel plates punched to have a predetermined shape in the motor axial direction (arrow A1 and arrow A2 directions). As a result, the motor core 84 is formed with a teeth portion 84A that extends outward in the radial direction of the motor (in the direction of the arrow R1) and around which the winding 26 is wound.

  The winding 26 is wound around the tooth portion 84A in layers, so that the winding portion 86 is formed along the tooth portion 84A. Further, the terminal portion of the winding 26 is connected to a circuit board 88 described later.

  An insulating member (not shown) is interposed between the winding portion 86 and the tooth portion 84A.

(Configuration of the circuit device 28)
As shown in FIG. 1, the circuit device 28 includes a circuit board 88 formed in a disk shape extending in the radial direction of the motor (arrow R1 and arrow R2 directions), and a plurality of circuits attached on the circuit board 88. Elements 90A and 90B are configured as main elements. In addition, the circuit element 90 </ b> A is disposed at a substantially central portion of the circuit board 88.

  Further, the surface opposite to the surface on which the circuit elements 90A and 90B are mounted on the circuit board 88 (the surface on the arrow A1 direction side) is the mounting surface 46A (can portion) of the motor housing 24 via the heat dissipation sheet 94 (silicon). (The bottom wall 46 of 42) (the central portion of the circuit board 88 is joined to the mounting surface 46A of the motor housing 24). As a result, the circuit device 28 (circuit board 88) is attached to the motor housing 24. Further, in a state where the circuit device 28 is attached to the motor housing 24, the circuit element 90 </ b> A is disposed at a portion facing the attachment surface 46 </ b> A (the bottom wall 46 of the can portion 42) of the motor housing 24. In other words, the circuit element 90 </ b> A is attached to a portion where the circuit board 88 and the bottom wall 46 of the can portion 42 are joined.

  The circuit device 28 is covered with the cover member 92 when the cover member 92 is attached to the motor housing 24.

(Configuration of impeller 18)
As shown in FIGS. 4A and 4B, the impeller 18 includes a first disk part 78 and a second disk part 80 formed in a disk shape, and a space between the first disk part 78 and the second disk part 80. It is an integrally molded component having a plurality of erected blades 82.

  The first disk portion 78 extends in the radial direction of the motor (arrow R1 and arrow R2 directions) and is formed in a circular shape when viewed from the motor axial direction (arrow A1 and arrow A2 directions). In addition, a protrusion 100 is formed at the center of the first disk portion 78 so as to protrude toward one side (arrow A1 direction) in the axial direction of the motor and the front end side in the protruding direction gradually narrows.

  The second disk portion 80 is disposed so as to face the first disk portion 78 described above, and the second disk portion 80 is inclined and extended toward the first disk portion 78 toward the radially outer side. Yes. Further, a circular opening 102 is formed in the axial center of the second disk portion 80, and an inner peripheral edge 102A of the opening 102 is directed toward one side (arrow A1 direction) of the motor in the axial direction. The flange portion 104 is bent. Further, the inner diameter D1 of the opening portion 102 (flange portion 104) is 16 mm, and the inner diameter of the inlet pipe 30 (see FIG. 1) arranged coaxially with the opening portion 102 and the flange portion 104 is also 16 mm. .

  Further, in the impeller 18 of the present embodiment, (distance b2 between the outer peripheral end 106 of the first disc portion 78 and the outer peripheral end 108 of the second disc portion 80) / (the inner peripheral portion 102A of the opening 102 and the first disc portion). The inclination angle of the second disk portion 80 is set so that the distance b1) to 78 is 0.7.

  As shown in FIG. 4B, the blade 82 is formed in an arc shape extending radially outward of the first disk portion 78 and the second disk portion 80, and both end portions (the outer peripheral end portion 110 and the outer end portion 110 and the second disk portion 80). The inner peripheral edge 112) is sharpened at an acute angle. Further, the outlet (outer peripheral end 110) of the blade 82 is located in a direction opposite to the rotation direction (arrow R3 direction) of the impeller 18 relative to the inlet (inner peripheral end 112) of the blade 82. Further, in the present embodiment, as shown in FIGS. 5A and 5B, the inlet angle β1 of the blade 82 is set to 35 deg, and the outlet angle β2 of the blade 82 is set to 18 deg. More specifically, an angle β1 formed by a surface 112A on the arrow R3 direction (rotation direction of the impeller 18) side of the inner peripheral end 112 of the blade 82 and a tangent in the rotation direction of the impeller 18 is set to 35 deg. An angle β2 formed by a surface 110A on the arrow R3 direction (rotation direction of the impeller 18) side of the outer peripheral end 110 of the blade 82 and a tangent line in the rotation direction of the impeller 18 is set to 18 deg.

  In addition, the outer diameter of the 1st disk part 78 and the 2nd disk part 80 of the impeller 18 of this embodiment is set to 44 mm.

(Operation and effect of this embodiment)
Next, the operation and effect of this embodiment will be described.

  As shown in FIG. 1, in this embodiment, when the rotor 20 rotates, the impeller 18 attached to the output shaft 72 of the rotor 20 rotates. As a result, the pump unit 14 is driven, and the cooling water flowing from the inlet pipe 30 of the pump case 16 is pumped toward the outlet pipe 32.

  Incidentally, as shown in FIGS. 4A, 4B, and 5A, in the present embodiment, the inner diameter of the opening 102 formed in the second disk portion 80 constituting a part of the impeller 18 is set to 16 mm. At the same time, the inlet angle β1 of the blade 82 constituting the other part of the impeller 18 is set to 35 deg. Therefore, the difference between the flow angle of the cooling water at the inlet of the impeller 18 (the inner peripheral end 112 of the blade 82) and the inlet angle β1 of the blade 82 (the angle of the inner peripheral end 112 of the blade) is reduced. Thereby, in this embodiment, the pressure loss of the cooling water in the inlet_port | entrance of the blade | wing 82 can be suppressed, without reducing the thickness of the inner peripheral end part 112 of the blade | wing 82. FIG.

  Here, the graph of FIG. 7 shows the relationship between the inlet angle β1 of the blade 82, the pump efficiency, and the discharge pressure. As shown in this figure, in this embodiment, the inlet angle β1 of the blade 82 is set in the range of 30 to 40 degrees. Therefore, in the electric pump 12 of this embodiment, the pump efficiency can be improved while preventing the discharge pressure from being lowered as much as possible. Further, as shown in this graph, when the inlet angle β1 of the blade 82 is set to 35 deg or more, the pump efficiency is maximized. In the present embodiment, since the inlet angle β1 of the blade 82 is set to 35 deg, the electric pump 12 with higher pump efficiency can be obtained. In addition, the range of the inner diameter D1 of the opening part 102 which confirmed that the relationship of FIG. 7 was acquired in the analysis by numerical fluid dynamics is the range of 14-20 mm.

  4A, FIG. 4B, and FIG. 5B, in this embodiment, the exit angle β2 of the blade 82 is set to 18 deg that is 22 deg or less, and (the outer peripheral end 106 of the first disc portion 78 and The value of distance b2) between the outer peripheral edge 108 of the second disk portion 80) / (distance b1 between the inner peripheral edge portion 102A of the opening 102 and the first disk portion 78) is in the range of 0.6 to 0.8. 7 is set. Therefore, as shown in FIG. 8A, the radial component of the flow velocity of the cooling water flowing out from the outlet of the impeller 18 (the outer peripheral end 110 of the blade 82) decreases, and as shown in FIG. Since the vortex generated in step 1 is weakened (since the vorticity is reduced), the pressure loss generated in the spiral chamber 37 can be suppressed. When the value of b2 / b1 is 0.5 outside the above range, as shown in FIGS. 12A and 12B, the outlet of the impeller 18 (the outer peripheral end portion 110 of the blade 82 is compared with the present embodiment). ), The radial component of the flow velocity of the cooling water flowing out from the gas increases, and the vorticity in the spiral chamber 37 increases.

  Summarizing the effects of setting the above-described values of the exit angles β2 and b2 / b1 of the blades 82 within the above ranges, the exit angles β2 and b2 / b1 of the blades 82 are shown in FIGS. By setting this value in the above range, the pump efficiency can be improved while preventing the discharge pressure from being lowered as much as possible. In addition, the range of the internal diameter D1 of the opening part 102 which confirmed that the relationship of the graph of FIG.8 and FIG.9 was acquired in the analysis by numerical fluid dynamics is the range of 14-20 mm.

  In addition, the graph of FIG. 11 shows the relationship between the inner diameter D1 of the opening 102 formed in the second disk portion 80, the pump efficiency, and the discharge pressure. As shown in this figure, it can be seen that when the inner diameter D1 of the opening 102 is in the range of 14 to 20 mm, the pump efficiency is further improved when the inner diameter D1 of the opening 102 is set to 16 to 18 mm. In this embodiment, it is set as the internal diameter D1 (16 mm) of the opening part 102 which pump efficiency improves more. Therefore, in this embodiment, the electric pump 12 with higher pump efficiency can be obtained.

  In the present embodiment, the maximum radius D of the spiral chamber 37 is set to 32 mm, the inner diameter D1 of the opening 102 is set to 16 mm, the inlet angle β1 of the blade 82 is set to 35 deg, and the outlet angle β2 of the blade 82 is set. Has been set to 18 deg and the value of b2 / b1 is set to 0.7, but the present invention is not limited to this. That is, the values of the maximum radius D of the spiral chamber 37, the inner diameter D1 of the opening 102, the inlet angle β1 of the blade 82, the outlet angle β2 of the blade 82, and b2 / b1 are changed within a range that satisfies the required pump performance. May be. In addition, the dimensions of the other parts may be appropriately set within a range that satisfies the required pump performance.

  Although one embodiment of the present invention has been described above, the present invention is not limited to the above, and various modifications other than the above can be implemented without departing from the spirit of the present invention. Of course.

DESCRIPTION OF SYMBOLS 12 ... Electric pump (pump apparatus for vehicles), 16 ... Pump case, 18 ... Impeller (blade), 30 ... Inlet pipe (inflow part), 32 ... Outlet pipe (outlet part), 37 ... Spiral chamber, 78 ... 1st Disc part: 80 ... Second disc part, 82 ... Blade, 102 ... Opening part, 102A ... Inner peripheral edge part of the opening part, 106 ... Outer peripheral edge of the first disc part, 108 ... Outer peripheral edge of the second disc part, R ... Maximum radius of swirl chamber, D1 ... inner diameter of opening, β1 ... blade inlet angle, β2 ... blade outlet angle, b1 ... distance between inner peripheral edge of opening and first disk part, b2 ... first disk part The distance between the outer peripheral edge of the steel and the outer peripheral edge of the second disk

Claims (2)

An inflow portion for allowing the working fluid to flow into the central portion in the radial direction, an outflow portion that is provided in a radially outer portion and from which the working fluid that has flowed in from the inflow portion flows out, and a spiral chamber that gradually increases in diameter along the circumferential direction And a pump case having
The pump case is rotatably supported. The first disk part is formed in a disk shape. The first disk part is opposed to the first disk part and is formed in a disk shape. The shaft part is circular. A second disk portion having a plurality of openings, and standing between the first disk portion and the second disk portion and extending outward in the radial direction of the first disk portion and the second disk portion. An impeller that pumps a working fluid from the inflow portion toward the outflow portion by rotating around an axis.
Have
The flow rate is 10 to 30 L / min, the discharge pressure is 30 to 80 kPa, and the specific speed (m, m ³ / min, min ⁻¹ ) is operated in the range of 100 to 300,
The maximum radius of the spiral chamber is 35 mm or less,
The inner diameter of the opening is 14 to 20 mm,
The inlet angle of the blade is in the range of 30-40 deg;
The exit angle of the blade is set to 22 deg or less,
(Distance b2 between the outer peripheral edge of the first disk part and the outer peripheral edge of the second disk part) / (Distance b1 between the inner peripheral edge part of the opening and the first disk part) is 0.6-0. 8 range,
Vehicle pump device. The inner diameter of the opening is 16 to 18 mm,
The inlet angle of the blade is 35 deg or more,
The vehicle pump device according to claim 1.