JP2015083815A - Pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pump device which reduces noise, and can suppress lowering of pump efficiency by regulating a position of a rotor in a pump case by a simple configuration.SOLUTION: In a pump device 1, a rotor 23 having a blade part 21 formed at an end part of an outer peripheral side is arranged in a rotor arrangement chamber 20 which is formed between a first case 11 and a second case 12 of a pump case 2. One end of a support shaft 24 which rotatably supports the rotor 23 is supported by the first case 11, and the other end is supported by the second case 12. When the rotor 23 is rotated, a vortex flow is generated in a circular arc vortex chamber 31 (first vortex chamber 31a and second vortex chamber 31b) arranged at the outer peripheral part of the rotor arrangement chamber 20, and a fluid is pressure-fed. The support shaft 24 is installed while being inclined with respect to a center axial line direction of the vortex chamber 31. When the rotor 23 rotates, the rotor 23 is energized toward one end side of the support shaft 24 by side pressure which is applied to the rotor 23.

Description

  The present invention relates to a pump device that sucks fluid into a pump case by rotating a rotor having blade portions formed on the outer peripheral end portion, and pressurizes and discharges the fluid.

  Patent Document 1 discloses a pumping device for fluid pressure called a vortex pump or a cascade pump. The pump device (cascade pump device) of the same document is supported at both ends by a pump case in which a rotor arrangement chamber (pump chamber) having a vortex chamber extending in an arc shape in the circumferential direction is formed at the outer periphery, and the pump case. A support shaft, a rotor that is rotatably attached to the support shaft, and a stator that is disposed coaxially with the rotor. A blade portion is formed at the outer peripheral end of the rotor, and a magnetic drive mechanism that rotationally drives the rotor is constituted by a magnet provided in the rotor and a drive coil provided in the stator. When the blades rotate, a vortex flow is generated in the vortex chamber, fluid is sucked from the suction port provided at one end in the circumferential direction of the vortex flow chamber, pressurized and discharged from the discharge port provided at the other end in the circumferential direction. The

JP2013-047510A

  In the cascade pump device of Patent Document 1, the fluid pressure in the vortex chamber is the lowest pressure near the suction port and the highest pressure near the discharge port. For this reason, the blade portion is pushed in the direction from the discharge port to the suction port by the fluid pressure. Further, in this type of cascade pump device, there are dimensional errors of parts and errors during assembly, so it is difficult to perfectly match the center axis of the rotor with the center axis of the vortex chamber. It is attached to the center axis of the vortex chamber so as to be inclined within the range of dimensional error and assembly error. Here, when the support shaft and the rotor are inclined with respect to the central axis direction of the vortex chamber, the blade portion is inclined in the vortex chamber, so that a part of the fluid pressure acting on the blade portion causes the rotor to rotate about its axis of rotation. It becomes a biasing force that biases in the direction. At this time, the direction of the urging force, that is, whether the rotor is urged to one side or the other side in the rotational axis direction is determined by the direction in which the rotor and the support shaft are tilted.

  In Patent Document 1, it is not determined in which direction the rotor and the spindle are inclined with respect to the central axis of the vortex chamber, and the inclination direction of the rotor and the spindle is unstable. Therefore, it cannot be controlled by the fluid pressure whether the rotor moves to one side or the other side in the rotation axis direction during rotation.

  In cascade pump devices, problems such as reduced pump efficiency and noise caused by contact between the pump case and the rotor when the rotor is tilted in the rotational axis direction and the positional accuracy of the rotor in the rotor arrangement chamber (pump chamber) decreases. Occurs. It may be possible to avoid rattling of the rotor and contact with the pump case by supporting both ends of the rotor in the axial direction of the rotor by thrust bearings provided on the pump case.However, thrust bearings are provided on both sides of the rotor in the axial direction. If provided, the number of parts will increase.

  Further, a seal portion having a narrow gap between the pump case and the rotor is formed on the inner peripheral side of the vortex chamber. Therefore, it is desirable that the rotor be positioned in the direction of the rotation axis so that contact at the seal portion can be avoided and the clearance at the seal portion can be maintained with the required accuracy. It is necessary to attach the thrust bearing with high accuracy, and it is necessary to increase the processing accuracy of the parts. Therefore, the cost increases.

  In view of the above problems, an object of the present invention is to provide a pump device that can suppress noise reduction and pump efficiency reduction by defining the position of the rotor in the pump case with a simple configuration.

  In order to solve the above-described problems, a pump device according to the present invention includes a rotor having a plurality of blade portions provided in a circumferential direction at an outer peripheral side end portion, a magnet held by the rotor, and a stator constituting a magnetic drive mechanism. A rotor arrangement chamber in which the rotor is arranged, a vortex chamber that extends in an arc shape in the circumferential direction on the outer peripheral side of the rotor arrangement chamber, and has both ends communicating with the suction port and the discharge port, respectively, and the rotation center axis of the rotor A pump case provided with a first shaft support portion for supporting one end of the rotor and a second shaft support portion for supporting the other end of the rotation center shaft, and when the rotor rotates, the rotor is rotated about the rotation center axis of the rotor. Biasing force generating means for generating a fluid pressure that biases toward the one side.

  According to the present invention, a fluid pressure acting on the rotor is generated by the biasing force generating means during rotation of the rotor, and the rotor is biased toward a predetermined direction (one side of the rotation center axis) by the fluid pressure, The rotor is positioned in the direction of the rotation center axis with respect to the pump case. For this reason, it is possible to avoid rattling in the axial direction of the rotor during rotation without using high-precision components. Therefore, it is possible to reduce noise due to contact between the rotor and the pump case, and it is possible to suppress a decrease in pump efficiency due to a decrease in the positional accuracy of the rotor.

  In the present invention, the pump case includes a first case provided with the first shaft support portion and a second shaft support portion provided between the first case and the rotor arrangement chamber. The first case includes a first rotor-side seal portion provided on a radially inner side of the blade portion of one end surface of the rotation center axis of the rotor. It is desirable that a first case-side seal portion facing in the rotation center axis direction is formed. In this case, since the first case side seal portion can be formed integrally with the first shaft support portion, even when the clearance between the first case side seal portion and the first rotor side seal portion is set to be small, By increasing the positional accuracy, contact between the rotor and the first case can be avoided.

  In the present invention, the first case side seal portion is adjacent to the vortex chamber on the radially inner side, and the clearance between the first case and the rotor is the rotor side seal portion and the first case side seal. It is desirable to minimize the part. By providing a seal in the part adjacent to the vortex chamber, it is possible to suppress the leakage of fluid from the vortex chamber and suppress the reduction in pump efficiency, but this part is on the outer periphery side of the rotor, and the peripheral speed is high during rotation. The noise generated when the rotor contacts the first case is large. However, in the present invention, since the contact between the rotor and the pump case can be avoided, it is possible to reduce noise while suppressing a decrease in pump efficiency.

  In the present invention, the stator is disposed at a position overlapping the rotation center axis when viewed from the radial direction, and in the rotation center axis direction, the magnetic center of the stator is urged against the magnetic center of the rotor. It is desirable that the rotor is displaced toward the urging direction of the rotor by the generating means. In this way, the direction in which the rotor is biased by the magnetic attractive force coincides with the direction in which the rotor is biased during rotation. Therefore, it is possible to prevent the rotor from rattling at the time of starting, and thus noise at the time of starting can be reduced. In addition, since the rotation center shaft and the stator overlap each other when viewed from the radial direction, it is easy to shift the magnetic center of the stator toward the first case with respect to the magnetic center of the rotor, and the pump device can be made thinner. Is also advantageous.

  In the present invention, the first case includes a partition wall that separates the stator from the rotor arrangement chamber, and the partition wall includes a bottomed tube portion on which the first shaft support portion is formed, and the stator It is desirable that the power supply substrate to be disposed on the radially outer side of the cylindrical portion. In this way, the first shaft support portion (shaft hole) can be lengthened by the thickness of the substrate. Alternatively, it is possible to arrange a plurality of thrust bearings that support the rotor. Therefore, the positional accuracy of the rotor can be improved.

  In the present invention, the rotation center shaft is a support shaft whose both ends are fixed to the first shaft support portion and the second shaft support portion, and the rotation of the cylindrical bearing portion that fits on the support shaft in the rotor. Between the end surface on one side of the central axis and the first case, an annular thrust bearing fitted to the support shaft is disposed, and a portion of the support shaft where the thrust bearing fits and the cylindrical bearing It is desirable that the part fits the same diameter. If it does in this way, when adjusting the position of the rotor in the axial direction, it is possible to cope with such a method as changing the thickness of the thrust bearing or arranging a plurality of thrust bearings in an overlapping manner.

  In the present invention, the urging force generating means is configured such that the first shaft support portion and the second shaft support portion are displaced in a direction intersecting with the central axis of the vortex chamber. If it does in this way, a rotation center axis | shaft can be installed in the state inclined in a predetermined direction with respect to the axial direction of a vortex chamber, and a rotor will be urged | biased by the predetermined direction at the time of rotation of a rotor. Therefore, rattling in the axial direction of the rotor during rotation can be avoided, and the positional accuracy of the rotor can be increased.

  In the present invention, the urging force generating means may be configured such that the second shaft support portion is shifted in a direction from the suction port toward the discharge port with respect to the first shaft support portion. If it does in this way, a rotor will be urged | biased toward the 1st axis | shaft support part arrange | positioned at the low voltage | pressure side (suction inlet side). Therefore, the rotor can be positioned with respect to the first case, and the position accuracy can be improved by avoiding rattling in the axial direction of the rotor during rotation.

  In this case, the first shaft support portion and the second shaft support portion are shaft holes that are recessed in parallel to the central axis of the vortex chamber, and the rotation center shaft is connected to the first shaft support portion. It is desirable to press fit. Thus, the press-fitting and fixing can improve the positional accuracy in the radial direction of the rotation center axis with respect to the first case. Further, since the other end of the rotation center shaft is inserted obliquely with respect to the shaft hole (second shaft support portion) on the second case side, the radial position accuracy of the rotation center shaft with respect to the second case is also increased. Therefore, the positional accuracy in the radial direction of the rotor can be increased. In addition, since it is not necessary to form the shaft hole in consideration of the inclination of the rotation center shaft, the first case and the second case can be easily manufactured.

  In the present invention, the biasing force generating means is an inclined channel formed in the rotor with an inclined surface inclined in the circumferential direction. If it does in this way, when a rotor rotates, a fluid will flow through an inclined flow path, and the rotor will be urged | biased toward the one end side of a rotation center axis | shaft by the fluid pressure which acts on an inclined surface at this time. Therefore, rattling in the axial direction of the rotor during rotation can be avoided, and the positional accuracy of the rotor can be increased.

  In this case, it is desirable that the inclined flow paths are arranged at equiangular intervals at a plurality of locations in the circumferential direction. In this way, even when one of the inclined channels overlaps the seal portion in the circumferential direction, the fluid flows through the other inclined channels. Therefore, the rotor can always be urged in the axial direction. In addition, since the moment acting in the direction in which the rotor tilts can be canceled, changes in the tilt of the rotor and the rotation center axis can be suppressed.

  In the present invention, the inclined flow path includes a first opening that opens at one end face of the rotation center axis of the rotor, and a second opening that opens at the other end face of the rotation center axis of the rotor; It is desirable to have. If it does in this way, an axial flow will flow into an inclined channel. In this case, it is desirable that the entire inclined surface overlaps one of the first opening and the second opening when viewed from the rotation center axis direction. In this way, when the entire inclined surface is exposed as viewed from the axial direction, the rotor can be formed by a mold that is divided into two in the axial direction without using a slide mold. Therefore, it is easy to manufacture the rotor.

  In this case, the first opening and the second opening are formed at radial positions overlapping with the vortex chamber in the rotor when viewed from the axial direction of the rotation center, and the periphery of the first opening and the second opening The opening width in the direction is preferably smaller than the width in the circumferential direction of the arc-shaped seal portion in which the vortex chamber is not formed in the circumferential direction. If it does in this way, it can control that a fluid leaks between an outlet and an inlet via an inclined channel. Therefore, a decrease in pump efficiency can be suppressed.

  In the present invention, the inclined flow path is formed in a groove shape at the outer peripheral side end of the rotor. In this case, since the peripheral speed of the portion where the inclined channel is formed is large, the flow velocity of the fluid passing through the inclined channel is large, and the fluid pressure acting on the inclined surface is large. Therefore, the urging force acting on the rotor can be increased, and the rattling of the rotor and the reduction in pump efficiency can be further reduced.

  In the present invention, the inclined channel is a through channel that penetrates the rotor radially inward from the blade portion. If it does in this way, since a blade | wing part can be provided in the perimeter of a rotor, the fall of pump efficiency can be suppressed.

  In this case, the through flow path is formed radially inward between the rotor and the pump case between a seal portion provided radially inward of the blade portion, and the seal portion includes the seal It is desirable that a short-circuit groove that communicates the radially inner side and the radially outer side of the portion is formed. If it does in this way, when pumping a liquid with a pump apparatus, the air which penetrate | invaded the vortex | eddy_current chamber can be guide | induced to an inner peripheral side through a short circuit groove | channel, and can be discharged | emitted from a penetration flow path to the discharge outlet side.

  According to the present invention, a fluid pressure acting on the rotor is generated by the urging force generator when the rotor rotates, and the rotor is urged toward a predetermined direction (one side of the rotation center axis) by the fluid pressure, The rotor is positioned with respect to the pump case. For this reason, shakiness in the axial direction of the rotor during rotation can be avoided without using high-precision components, and the positional accuracy of the rotor can be increased. Therefore, it is possible to reduce noise due to contact between the rotor and the pump case, and it is possible to suppress a decrease in pump efficiency due to a decrease in the positional accuracy of the rotor.

It is explanatory drawing of the pump apparatus of Embodiment 1 to which this invention is applied. It is sectional drawing of the pump apparatus of Embodiment 1 to which this invention is applied. It is an exploded sectional view of a pump case, a rotor, and a spindle. It is a perspective view of the 1st case and the 2nd case. It is explanatory drawing of a rotor. It is a perspective view of a stator. It is explanatory drawing of the urging | biasing force generation means of Embodiment 1. FIG. It is explanatory drawing of the urging | biasing force generation means of Embodiment 2. FIG. It is explanatory drawing of the urging | biasing force generation | occurrence | production means of Embodiment 3.

(Embodiment 1)
The pump device according to Embodiment 1 of the present invention will be described below with reference to the drawings. FIG. 1 is an explanatory diagram of a pump device according to a first embodiment to which the present invention is applied. FIG. 1 (a) shows a plan view of the pump device viewed from one side in the axial direction, and FIG. The bottom view which looked at the pump apparatus from the other side of the axial direction is shown. 2A and 2B are cross-sectional views of the pump device according to the first embodiment. FIG. 2A is a cross-sectional view taken along the line AA in FIG. 1A, and FIG. It is a partial expanded sectional view of the area | region E) of a). The pump device 1 according to the first embodiment is a cascade pump device that pumps a fluid such as a liquid. The pump device 1 is built in an electronic device and is used for circulating water as a refrigerant for cooling a CPU or the like. In addition, other fluids can be pumped by the pump device 1 and can be used for other purposes.

  The pump device 1 includes a flat quadrangular prism-shaped pump case 2 as a whole. The pump case 2 is made of resin and is made of PPS (polyphenylene sulfide) or the like. The pump device 1 includes a first end face 2a located on one side L1 in the axis L direction (height direction) and a second end face 2b located on the other side L2 in the axis L direction. The inner peripheral portion of the first end surface 2 a is configured by a sealant 16 described later, and the outer peripheral edge of the first end surface 2 a and the second end surface 2 b are configured by the pump case 2. Here, the axis L of the pump device 1 indicates a central axis of an arc-shaped vortex chamber 31 described later provided in the pump case 2.

(Pump case)
The pump case 2 includes a first side surface 2c in which the suction pipe 3 and the discharge pipe 4 project in parallel, and a second end face 2b as outer peripheral surfaces constituting the contour of the pump case 2 when viewed from the axis L direction. When viewed from the side, the second side surface 2d adjacent to the first side surface 2c in the counterclockwise direction, the third side surface 2e located on the back side of the second side surface 2d, and the back side of the first side surface 2c are located. A fourth side surface 2f is provided. In the corner portion between the first side surface 2 c and the second side surface 2 d of the pump case 2, a wiring extraction portion 6 for taking out the lead wire 5 from the inside of the pump case 2 is provided.

  The lead wire 5 is drawn out in the diagonal direction of the planar shape when the pump case 2 is viewed in the direction of the axis L through the wiring extraction portion 6. The lead wire 5 extends longer than the suction pipe 3 and the discharge pipe 4, and a connector 7 is attached to the tip thereof. The suction pipe 3, the discharge pipe 4, and the wiring extraction portion 6 are located between the first end face 2 a and the second end face 2 b located within the height range of the pump case 2, that is, at both ends in the axis L direction of the pump case 2. Is provided. A fixing member 6a for fixing the lead wire 5 sandwiched between the wiring outlet 6 (not shown) formed by cutting out the pump case 2 is attached to the wiring outlet 6.

  An inclined surface 2k is formed at the corner portion between the first side surface 2c and the second side surface 2d where the wiring lead-out portion 6 is provided, with the tip of the corner portion cut obliquely. Further, a hook 8 extending in parallel with the inclined surface 2k from the first side surface 2c side is provided at the corner portion. A gap for locking the lead wire 5 is formed between the inclined surface 2k and the hook 8. The hook 8 is located at an intermediate portion in the axis L direction of the inclined surface 2k. By engaging the lead wire 5 in the gap between the hook 8 and the inclined surface 2k, the lead wire 5 is pulled out from the wiring extraction portion 6 located on one side L1 (the first end surface 2a side) of the inclined surface 2k in the axis L direction. The lead wire 5 can be routed to the other side L2 (the second end face 2b side) in the axis L direction. FIG. 1 and FIG. 2A illustrate a state in which the lead wire 5 is extended from the wiring take-out portion 6 without being changed in direction by being locked to the hook 8.

  Mounting holes 9 penetrating the pump case 2 in the direction of the axis L are formed in the corner portion between the second side surface 2d and the fourth side surface 2f and the corner portion between the third side surface 2e and the first side surface 2c. ing. The attachment hole 9 is used as an attachment portion when the pump device 1 is attached to an external device.

  FIG. 3 is an exploded sectional view of the pump case, the rotor, and the support shaft. 4 is a perspective view of the first case and the second case, FIG. 4 (a) is a perspective view of the second case as viewed from the rotor arrangement chamber side, and FIG. 4 (b) is the first case of the rotor arrangement chamber side. It is the perspective view seen from. The pump case 2 includes a first case 11 and a second case 12 stacked in the direction of the axis L. The first case 11 is disposed on one side L1 in the direction of the axis L, and constitutes the outer peripheral edge of the first end face 2a of the pump case 2. The second case 12 is disposed on the other side L <b> 2 in the direction of the axis L, and constitutes the second end surface 2 b of the pump case 2. The wiring extraction part 6 is provided at a corner portion of the first case 11. As shown in FIG. 4A, the suction pipe 3 and the discharge pipe 4 protrude from the side surface of the second case 12, and the hook 8 is provided at a corner portion of the second case 12. The suction pipe 3, the discharge pipe 4 and the hook 8 provided in the second case 12 are made of resin, and are formed integrally with the second case 12 by molding.

  An anti-rotation mechanism 13 for preventing the relative rotation of the second case 12 and the first case 11 when laminating the second case 12 and the first case 11 is provided at a corner portion of the pump case 2 that is diagonally opposite to the wiring extraction portion 6 (FIG. 1 ( b)) is provided. The anti-rotation mechanism 13 is configured by an anti-rotation protrusion 13a (see FIG. 4B) provided on the first case 11 and an anti-rotation recess 13b (see FIG. 4A) provided on the second case 12. Has been. A case fixing portion 14 is provided between the suction pipe 3 and the discharge pipe 4 of the pump case 2 so as to protrude from the first side face 2c (see FIGS. 1A and 1B). The case fixing portion 14 is a portion for fixing the second case 12 and the first case 11 using screws, and includes a first protrusion 14A (see FIG. 4B) provided on the first case 11, A second protrusion 14B (see FIG. 4A) provided on the two cases 12 is provided. A screw hole 10b (see FIG. 4B) is formed in the first protrusion 14A, and a through-hole 10a (see FIG. 4A) is formed in the second protrusion 14B. As shown in FIGS. 4A and 4B, the first case 11 has three through holes 10a, and the second case 12 has three screw holes 10b at positions overlapping with the through holes 10a. Has been. One set of these three sets of through holes 10 a and screw holes 10 b is formed in the case fixing portion 14.

(Rotor placement room)
As shown in FIG. 2A, a rotor arrangement chamber 20 is configured between the second case 12 and the first case 11. A rotor 23 and a support shaft 24 that rotatably supports the rotor 23 are arranged in the rotor arrangement chamber 20, and a blade portion 21 is configured at the outer peripheral side end of the rotor 23. The rotor 23 holds a drive magnet 22. The outer peripheral part of the rotor arrangement | positioning chamber 20 becomes the annular | circular shaped flow path formation part 25, The blade | wing part 21 is inserted here. Between the second case 12 and the first case 11, an O-ring 26 is arranged along the outer periphery of the rotor arrangement chamber 20. The O-ring 26 seals the gap between the second case 12 and the first case 11.

  On one side L1 of the first case 11 in the direction of the axis L, that is, on the side opposite to the rotor arrangement chamber 20 side of the first case 11 (the side opposite to the second case 12), the stator 29 and the power supply substrate 30 are arranged. ing. The stator 29 includes a drive coil 27 and a stator core 28 on which the drive coil 27 is mounted. In addition, the power supply board 30 is equipped with an electronic element that controls the excitation current to the drive coil 27. The drive magnet 22 mounted on the rotor 23 and the drive coil 27 mounted on the stator 29 constitute a magnetic drive mechanism for rotationally driving the blade portion 21 provided on the rotor 23. When viewed from the direction of the axis L, the magnetic drive mechanism is disposed radially inward from the flow path forming portion 25. The first case 11 is disposed between the rotor 23 and the stator 29, and functions as a partition that separates the energized portions such as the stator 29 and the power supply substrate 30 from the rotor arrangement chamber 20.

  The flow path forming portion 25 is formed with a vortex chamber 31 extending in an arc shape in the circumferential direction over a predetermined angular range around the axis L. More specifically, a first vortex chamber 31a having a semicircular cross-sectional shape is formed in a region on one side L1 in the direction of the axis L in the flow path forming portion 25. The first case 11 is formed with a semicircular arc groove 34a constituting the first vortex chamber 31a. On the other hand, a second vortex chamber 31b that overlaps with the first vortex chamber 31a when viewed from the axis L direction is formed in the region on the other side L2 in the axis L direction in the flow path forming portion 25. The second vortex chamber 31b has a semicircular cross-sectional shape opposite to the first vortex chamber 31a, and a semicircular arc groove 34b constituting the second vortex chamber 31b is formed in the second case 12. In this embodiment, the vortex chamber 31 (the first vortex chamber 31a and the second vortex chamber 31b) is formed over an angular range exceeding 270 ° around the axis L.

  The flow path in the suction pipe 3 provided in the second case 12 is a suction flow path for supplying fluid to the vortex chamber 31. The second case 12 has a suction port 3 a that communicates the vortex chamber 31 (the first vortex chamber 31 a and the second vortex chamber 31 b) and the flow path in the suction pipe 3 at one end in the circumferential direction of the vortex chamber 31. Is provided. Further, the second case 12 has a discharge port that communicates the vortex chamber 31 (the first vortex chamber 31a and the second vortex chamber 31b) and the flow path in the discharge pipe 4 at the other circumferential end of the vortex chamber 31. 4a is provided. The flow path in the discharge pipe 4 is a discharge flow path for discharging fluid from the vortex chamber 31. In the flow path forming portion 25, a portion located between the suction port 3 a and the discharge port 4 a is a blocking portion 32. The blocking portion 32 is provided in an angular range where the arcuate groove 34a of the first case 11 is not formed, and in an angular range where the arcuate groove 34b of the second case 12 is not formed. The second arc-shaped seal portion 32b is formed. In the angle range (blocking portion 32) where the first arc-shaped seal portion 32a and the second arc-shaped seal portion 32b are provided, fluid does not flow in the circumferential direction.

  As shown in FIGS. 2A and 3, a center portion of the first case 11 is provided with a bottomed cylindrical central projecting portion 80 projecting toward one side L <b> 1 in the axis L direction. A circular recess 81 that opens toward the second case 12 is formed in the central protrusion 80, and a first shaft support portion 82 that is a bottomed shaft hole is open on the bottom surface 81 a of the circular recess 81. The first shaft support portion 82 extends in the direction of the axis L at the distal end portion of the central protrusion 80, and the first shaft support portion 82 is located inside the end portion on one side L1 in the axis L direction. It is a bottomed cylindrical part formed. The support shaft 24 is made of stainless steel, and an end portion on one side L1 in the direction of the axis L is press-fitted and fixed to the first shaft support portion 82 as shown in FIG. Further, the second case 12 is formed with a second shaft support portion 60 that is a bottomed shaft hole at a position facing the first shaft support portion 82 in the axis L direction. An end portion of the other side L2 of the support shaft 24 in the axis L direction is fixed to the second shaft support portion 60. In this embodiment, the axis L of the pump device 1 passes through the radial center of the first shaft support portion 82. On the other hand, as will be described later, the radial center of the second shaft support portion 60 does not coincide with the axis L, and the first shaft support portion 82 and the second shaft support portion 60 are shifted in a direction intersecting the axis L direction. Has been.

  As shown in FIG. 2B, the outer peripheral edge of the end face on the other side L2 in the axis L direction of the support shaft 24 is chamfered over the entire circumference. The chamfered portion is provided with a tapered support shaft side guide surface 24a whose diameter is reduced toward the tip. The opening edge of the second shaft support portion 60 is provided with a tapered shaft hole side guide surface 60a having a diameter that increases toward one side L1 (the first case 11 side) in the axis L direction. Yes. Note that the support shaft side guide surface 24a and the shaft hole side guide surface 60a may be guide surfaces having a curved surface cut along a plane including the axis L. Further, as shown in FIG. 2A, the depth dimension of the second shaft support portion 60 into which the end portion of the other side L2 of the support shaft 24 is fitted is the one side L1 of the support shaft 24 in the axis L direction. The depth N0 of the press-fitting allowance to be press-fitted into the first shaft support portion 82 in the support shaft 24 is smaller than the depth size of the first shaft support portion 82 into which the end of the first shaft support portion is fitted. The dimension is set to be longer than the dimension N1 of the fitting allowance fitted into the support portion 60.

(Rotor)
5A and 5B are explanatory views of the rotor 23. FIG. 5A is a perspective view of the rotor 23, FIG. 5B is a bottom view seen from the other side L2 in the direction of the axis L, and FIG. FIG. The rotor 23 is made of a resin such as PPS, and as shown in FIGS. 2, 3, and 5, the disk portion 40 and a cylindrical bearing portion 41 that protrudes from the center of the disk portion 40 to one side L <b> 1 in the axis L direction. 2) and a cylindrical portion 42 that protrudes from the portion near the outer periphery of the disc portion 40 to the one side L1 in the axis L direction. The cylindrical portion 42 surrounds the cylindrical bearing portion 41 coaxially with a predetermined interval between the cylindrical bearing portion 41 and the cylindrical bearing portion 41. The interval between the cylindrical bearing portion 41 and the cylindrical portion 42 is an interval at which the stator 29 can be disposed therebetween via the first case 11. In the rotor 23, the support shaft 24 (rotation center shaft) is inserted into the center hole 41 a of the cylindrical bearing portion 41, and the cylindrical bearing portion 41 is formed inside the central protruding portion 80 of the first case 11. It is possible to rotate around the axis L of the support shaft 24 in a state where it is disposed in the position.

  As shown in FIG. 2A, one or more sheets are provided between the cylindrical bearing portion 41 of the rotor 23 and the bottom surface 81a of the circular recess 81 of the first case 11 in which the cylindrical bearing portion 41 is disposed. The washer 43 is arranged. The washer 43 is a thrust bearing that supports the rotor 23 from one side L1 in the axis L direction, and the position of the rotor 23 in the axis L direction is adjusted by the washer 43 being arranged. In this embodiment, two washers are inserted, but the thickness and number of washers can be appropriately adjusted. Further, the outer diameter of the support shaft 24 is constant, and the portion of the support shaft 24 where the washer 43 is mounted and the portion of the support shaft 24 inserted into the cylindrical bearing portion 41 have the same diameter. .

  A cylindrical yoke 44 is held on the inner peripheral surface of the cylindrical portion 42 of the rotor 23, and a cylindrical drive magnet 22 is held on the inner peripheral surface of the yoke 44. The yoke 44 is formed integrally with the rotor 23 by insert molding, and the drive magnet 22 is bonded to the yoke 44.

  As shown in FIGS. 3 and 5A to 5C, the disk part 40 includes an annular projecting part 45 projecting radially outward from the cylindrical part 42. A plurality of blade portions 21 are arranged in the circumferential direction on the outer peripheral edge of the annular projecting portion 45. That is, recesses 46a and 46b formed in two steps in the axis L direction are formed on the outer peripheral edge of the annular projecting portion 45 at equal angular intervals in the circumferential direction. The recess 46a is formed by cutting out the periphery of the end surface 45a facing the one side L1 in the axis L direction of the annular projecting portion 45 into an arc shape. The recess 46b is formed by cutting out the peripheral edge of the end surface 45b facing the other side L2 of the annular projecting portion 45 in the axis L direction into an arc shape. A partition plate 47 extending in the radial direction is formed between the recesses 46a adjacent in the circumferential direction and between the recesses 46b adjacent in the circumferential direction. Further, a rib 48 that extends in the circumferential direction and divides the partition plates 47 in the axis L direction is formed between the recess 46a and the recess 46b adjacent in the axis L direction. The recesses 46a and 46b have the same shape, and are formed symmetrically on one side L1 and the other side L2 of the rib 18 extending in the circumferential direction in the axis L direction. As shown in FIG. 2, the blade portion 21 is inserted into the flow path forming portion 25.

  The disk portion 40 is provided with an annular protrusion 40a that protrudes radially inward from the cylindrical portion 42 to the other side L2 in the axis L direction with respect to the annular protrusion 45, and the annular protrusion 40a has a plurality of through holes. 40b is formed at equiangular intervals in the circumferential direction. In this embodiment, six through holes 40b are formed. The number of through holes 40b can be changed as appropriate. The cross-sectional shape of the through hole 40b is circular and extends parallel to the direction of the axis L. The through hole 40b penetrates the annular protrusion 40a in the axis L direction.

(Stator)
FIG. 6 is a perspective view of the stator 29. The stator 29 includes an annular portion 50 and a stator core 28 having a plurality of salient poles 51 projecting radially outward from the annular portion 50, and a drive coil 27 wound around each of the plurality of salient poles 51 of the stator core 28. ing. As shown in FIG. 2A, the stator 29 is formed between the outer peripheral surface of the central projecting portion 80 and the cylindrical portion 89 provided on the outer periphery on one side L1 of the first case 11 in the axis L direction. It is arranged in the stator storage chamber 83 which is an annular concave portion. In this state, each salient pole 51 of the stator 29 faces the drive magnet 22 of the rotor 23 in the rotor arrangement chamber 20 via the first case 11 in a direction orthogonal to the axis L. Further, the cylindrical bearing portion 41 of the rotor 23 extends to a position overlapping with the drive magnet 22 when viewed from the radial direction, and the support shaft 24 attached to the cylindrical bearing portion 41 is viewed from the radial direction. The stator 29 is disposed so as to overlap the stator storage chamber 83.

  The stator core 28 is configured by laminating a plurality of identically shaped plate-like core pieces 52 formed by punching a thin plate-like magnetic steel plate in the vertical direction, and the lamination direction of the plate-like core pieces 52 is the direction of the axis L. It has become. On the inner peripheral surface of the annular portion 50 of the stator core 28, three inner concave portions 53 are formed around the axis L at equal angular intervals. On the other hand, on the outer peripheral surface of the central protrusion 80 of the first case 11 constituting the stator storage chamber 83, three protrusions (not shown) protruding radially outward are provided at equal angular intervals around the axis L. ing. The stator core 28 is fixed so as not to be relatively rotatable in the circumferential direction with respect to the central protrusion 80 by press-fitting these protrusions into the inner recess 53. A positioning portion (not shown) is provided on the outer peripheral surface of the central projecting portion 80 to contact the annular portion 50 of the stator core 28 from the other side L2 in the axis L direction to position the stator core 28 in the axis L direction. Yes.

  On one side L1 of the first case 11 in the direction of the axis L, a frame-shaped outer peripheral wall 86 is provided along the periphery of the first case 11, and the power supply substrate 30 is disposed in a space surrounded by the outer peripheral wall 86. ing. The power supply substrate 30 is disposed so as to overlap with one side L1 in the axis L direction with respect to the stator 29 disposed in the stator housing chamber 83. An opening 30 a is formed in the center of the power supply substrate 30, and the tip of the central protrusion 80 of the first case 11 is disposed in the opening 30 a. The first shaft support portion 82 provided in the central projecting portion 80 extends to a position where it overlaps the power supply substrate 30 when viewed from the radial direction.

  As shown in FIG. 1B and FIG. 2A, in the substrate arrangement space surrounded by the outer peripheral wall 86, insulation such as epoxy, acrylic, or silicon is used until the tip surface of the outer peripheral wall 86 is reached. A sealing agent 16 made of a conductive resin is poured. The stator 29 and the power supply substrate 30 are covered and fixed by the sealant 16. Note that the surface of the sealant 16 may be lower than the tip of the outer peripheral wall 86.

  When an excitation current is supplied from the connector 7 to the drive coil 27 via the lead wire 5 and the power supply substrate 30, the rotor 23 rotates about the axis L. As a result, the liquid is sucked from the suction pipe 3 into the first vortex chamber 31a and the second vortex chamber 31b, pressurized in the first vortex chamber 31a and the second vortex chamber 31b, and discharged from the discharge pipe 4 Is done. The motor (the rotor 23, the stator 29, and the power supply board 30) that drives the pump device 1 is a three-phase brushless motor. The power supply board 30 includes three hall elements (not shown) that detect the position of the drive magnet 22 of the rotor 23. One is arranged. When the order of the excitation currents supplied to the drive coil 27 is reversed, the rotor 23 rotates in the reverse direction, and the liquid is sucked from the discharge pipe 4 to be added in the first vortex chamber 31a and the second vortex chamber 31b. Pressure and discharged from the suction pipe 3.

(Second case)
As shown in FIGS. 3 and 4A, the second case 12 includes a bottom plate portion 61 constituting the second end surface 2b of the pump case 2 and an outer peripheral portion of the bottom plate portion 61 on one side L1 in the axis L direction. A side wall portion 62 that extends, and a circular recess 63 formed by the bottom plate portion 61 and the side wall portion 62 are provided. A region along the outer peripheral edge of the bottom of the circular recess 63 is a region in which the flow path forming unit 25 is configured in an annular shape. In the side wall 62, the suction pipe 3 and the discharge pipe 4 protrude in parallel from the surface constituting the first side surface 2c of the pump case 2 described above.

  The above-described second shaft support portion 60 is provided at the center of the bottom of the circular recess 63, and an annular recess 64 is formed coaxially on the outer peripheral side of the second shaft support portion 60. The second shaft support portion 60 is a bottomed shaft hole, and a tapered shaft hole side guide surface 60a is provided at the opening edge. An inner annular protrusion 65 is provided between the second shaft support portion 60 and the annular recess 64, and an outer annular protrusion 66 is provided on the outer peripheral side of the annular recess 64. The outer annular protrusion 66 includes an end surface 66a facing the other side L2 in the axis L direction, and along the outer peripheral edge of the end surface 66a, the arc groove 34b and the second arc-shaped seal constituting the second vortex chamber 31b. A portion 32b is provided.

  On the end face 66 a of the outer annular protrusion 66, the second vortex chamber 31 b (arc groove 34 b) and the portion adjacent to the radially inner side of the second arc-shaped seal portion 32 b are annular second case-side seal portions 67. is there. The second case side seal portion 67 is opposed to the end surface 45b facing the other side L2 in the axis L direction of the annular projecting portion 45 provided on the outer peripheral portion of the rotor 23 disposed in the rotor arrangement chamber 20 with a small gap G2. (See FIG. 2). That is, in the end face 45b, a portion adjacent to the inside in the radial direction of the blade portion 21 is a rotor-side seal portion. The second case-side seal portion 67 has a short-circuit groove 67a having a constant width that allows communication between the radially inner side (annular recess 64) and the radially outer side (second vortex chamber 31b) of the second case-side seal portion 67. Two are formed at positions apart from each other. When a liquid such as water is pumped as a fluid as in the present embodiment, the air that has entered the second vortex chamber 31b is guided to the inner peripheral side of the second case side seal portion 67 by the short-circuit groove 67a. Through the through hole 40 b provided in the disk portion 40 of the rotor 23, it is sent to the discharge port 4 a side and discharged from the pump case 2.

  The clearance between the second case 12 and the rotor 23 is set to be the smallest between the second case side seal portion 67 and the end face 45b. For example, the gap G2 is set so that the minimum value is 0.075 mm and the center value is 0.15 mm. The second case 12 is formed by molding a resin material, and the second case side seal portion 67 is integrated with the second shaft support portion 60.

  An annular step portion 68 is provided on the opening side portion of the inner peripheral surface of the circular recess 63. The annular step portion 68 includes an annular end surface 68a extending radially outward from an intermediate position in the axis L direction of the inner peripheral surface of the side wall portion 62 and facing the first case 11, and an axial line extending from the outer periphery of the annular end surface 68a. An inner peripheral surface 68b extending to one side L1 in the L direction is provided.

  Here, the second case 12 is an injection-molded product, and the gate at the time of molding is provided at the lower center of the bottom plate portion 61. That is, the gate is provided on the bottom plate portion 61 on the side opposite to the second shaft support portion 60. Accordingly, since the resin flows from the center of the second shaft support portion 60, the second shaft support portion 60 is formed with high dimensional accuracy.

(First case)
As shown in FIG. 4B, when the first case 11 is viewed from the other side L2 in the direction of the axis L, the inner annular protrusion 90 is formed surrounding the circular recess 81 in which the cylindrical bearing portion 41 is disposed. Yes. At the center of the inner annular protrusion 90, the circular recess 81 and the first shaft support portion 82 described above are formed coaxially. An outer annular protrusion 91 is coaxially formed on the outer peripheral side of the inner annular protrusion 90, and an annular recess 92 is provided between the inner annular protrusion 90 and the outer annular protrusion 91. On the outer peripheral side of the outer annular projecting portion 91, an overhanging portion 93 that projects in a direction orthogonal to the axis L direction is formed. The overhang portion 93 has a substantially rectangular outer shape when viewed from the direction of the axis L. An outer peripheral wall 86 surrounding the space in which the above-described power supply substrate 30 is disposed is formed on the outer peripheral edge of the surface on the one side L1 in the axis L direction in the overhang portion 93.

  An end surface 91a on the other side L2 in the axis L direction of the outer annular protrusion 91 is annular, and an arc groove 34a and a first arc-shaped seal portion 32a constituting the first vortex chamber 31a are formed on the end surface 91a. In the end surface 91a, the first vortex chamber 31a (arc groove 34a) and the portion adjacent to the radially inner side of the first arc-shaped seal portion 32a are annular first case-side seal portions 94. The first case side seal portion 94 opens a minute gap G1 from the end surface 45a facing the one side L1 in the axis L direction of the annular projecting portion 45 provided on the outer peripheral portion of the rotor 23 arranged in the rotor arrangement chamber 20. (Refer to FIG. 2A). That is, in the end face 45a, a portion adjacent to the inside in the radial direction of the blade portion 21 is a rotor-side seal portion.

  The clearance between the first case 11 and the rotor 23 is set to be the smallest between the first case side seal portion 94 and the end face 45a. For example, the gap G1 is set to have a minimum value of 0.075 mm and a center value of 0.10 mm, and the gap G1 is narrower than the gap G2 between the second case 12 and the rotor 23 described above. The first case 11 is formed by molding a resin material, and the first case side seal portion 94 is integrated with the first shaft support portion 82.

  An annular radial protrusion 96 is provided on the outer peripheral surface 95 of the outer annular protrusion 91. The radial projecting portion 96 includes an annular end surface 96a extending radially outward from an intermediate position in the axis L direction of the outer annular projecting portion 91 and facing the second case 12, and an axis L from the outer peripheral edge of the annular end surface 96a. An outer peripheral surface 96b extending to the other side L2 in the direction and facing radially outward is provided.

  Here, the first case 11 is an injection-molded product, and the gate at the time of molding is provided at the center of the central protrusion 80. That is, the gate is provided on the opposite side of the first shaft support portion 82 at the end portion on the one side L1 in the direction of the axis L in the central protrusion 80. Accordingly, since the resin flows from the center of the first shaft support portion 82, the first shaft support portion 82 is formed with high dimensional accuracy.

(Assembly method of pump case)
When the rotor arrangement chamber 20 is partitioned between the first case 11 and the second case 12, the O-ring 26 is mounted on the outer peripheral surface 95 of the outer annular protrusion 91 of the first case 11. At this time, a lubricant is applied to the O-ring 26. Further, one end of the support shaft 24 is press-fitted and fixed to the first shaft support portion 82 of the first case 11 in advance. The rotor 23 is disposed in the circular recess 63 of the second case 12 so that the support shaft 24 can be inserted into the cylindrical bearing portion 41.

  Next, the first case 11 and the second case 12 are brought close to each other, and the outer annular protrusion 91 of the first case 11 is inserted inside the annular step 68 of the second case 12. At this time, both cases are positioned in the circumferential direction so that the anti-rotation protrusion 13 a provided on the first case 11 is inserted into the anti-rotation recess 13 b provided on the second case 12. After an appropriate time, the 1st case 11 and the 2nd case 12 are made to approach relatively. At this time, the outer peripheral surface 96b of the radially projecting portion 96 of the first case 11 abuts on the inner peripheral surface 68b of the annular step portion 68 of the second case 12, and the first case 11 is in contact with the second case 12. Position in the radial direction. The end of the support shaft 24 is fitted into the second shaft support portion 60 with a slight delay from the time of positioning. At this time, as described above, the tapered support shaft side guide surface 24a is provided on the outer peripheral edge of the end surface of the support shaft 24, and the tapered shaft hole guide surface 60a is provided on the second shaft support portion 60. Therefore, fitting of the support shaft 24 to the second shaft support portion 60 is easily performed.

  After that, when the first case 11 and the second case 12 are further brought closer, a portion of the end surface 91a of the outer annular protrusion 91 that is adjacent to the inner side in the radial direction of the first vortex chamber 31a and the first arcuate seal portion 32a. However, the first case 11 is positioned with respect to the second case 12 in the direction of the axis L in contact with the inner peripheral portion of the annular end surface 68a of the annular step portion 68. Thereby, the rotor arrangement | positioning chamber 20 is formed between the 2nd case 12 and the 1st case 11, and the fitting to the 2nd axis | shaft support part 60 of the spindle 24 is completed. At this time, the O-ring 26 is disposed between the outer peripheral surface 95 of the outer annular protrusion 91 of the first case 11 and the second case 12 between the annular end surface 96 a of the radial protrusion 96 and the annular end surface 68 a of the annular step 68. It becomes the state crushed in the radial direction between the inner peripheral surfaces 68b of the annular step portion 68. Therefore, a state in which fluid leakage from the rotor arrangement chamber 20 is prevented is formed.

  After positioning the first case 11 with respect to the second case 12, the three cases that pass through the through-hole 10 a provided in the second case 12 and screw into the screw hole 10 b provided in the first case 11 are provided. The first case 11 and the second case 12 are fixed by the head screw.

  Thus, when the first case 11 is laminated on the second case 12 and the rotor arrangement chamber 20 is formed, the lower end of the support shaft 24 penetrating the cylindrical bearing portion 41 of the rotor 23 is The support shaft 24 and the central projecting portion 80 are coaxially inserted and fixed to the second shaft support portion 60 of the second case 12. And the blade part 21 provided in the outer peripheral part of the rotor 23 will be in the state inserted in the flow-path formation part 25, the 1st vortex chamber 31a is comprised in the one side L1 of the axial direction L of the blade part 21, and a blade part A second vortex chamber 31b is configured on the other side L2 of the axis 21 in the direction of the axis L.

  Further, by fixing both ends of the support shaft 24, the stator 29 and the rotor 23 are arranged coaxially, the salient pole 51 around which the drive coil 27 is wound in the stator core 28, and the rotor arranged in the rotor arrangement chamber 20. 23 drive magnets 22 face each other through the first case 11. Here, in this embodiment, as shown in FIG. 2, two washer 43 are inserted between the cylindrical bearing portion 41 of the rotor 23 and the bottom surface 81 a of the circular concave portion 81 in the first case 11, so that the stator core The magnetic center position in the axis L direction of the drive magnet 22 mounted on the rotor 23 is shifted to the other side L2 in the axis L direction with respect to the magnetic center position in the axis L direction of 28. Therefore, between the stator core 28 and the drive magnet 22, a magnetic attractive force that attracts the rotor 23 to one side L1 in the direction of the axis L acts. In this embodiment, the magnetism of the rotor 23 and the stator 29 is such that the urging direction of the rotor 23 by the magnetic attractive force is the same direction as the urging force acting on the rotor 23 when the fluid flows in the pump case 2. The center position is shifted.

  When the magnetic center positions of the rotor 23 and the stator 29 are shifted, the rotor 23 is positioned at a balance position between the magnetic attractive force and the gravity acting on the rotor 23 when the rotor 23 is stationary. Further, at the time of rotation, the rotor 23 is positioned at a balance position of magnetic attraction force, gravity, and fluid pressure in the first vortex chamber 31a and the second vortex chamber 31b. The direction of gravity acting on the rotor 23 is determined by the installation direction of the pump device 1. When the first case 11 is arranged on the lower side in this embodiment, both the magnetic attractive force and gravity are directed toward the first case 11. . Here, if the balance position between the magnetic attractive force and the gravity is set to be on the first case 11 side when stationary, the rattling of the rotor 23 at the time of activation can be suppressed. Further, if the magnetic attraction force is set to be larger than the gravity applied to the rotor 23, the rotor 23 can always be urged to the same side regardless of the installation direction of the pump device 1. Therefore, the influence of the installation direction of the pump device 1 can be avoided.

(Biasing force generation means)
Next, the biasing force generating means employed in the first embodiment will be described. FIG. 7 is an explanatory diagram of the urging force generating means, and FIG. 7A shows the radial center of the second shaft support 60 in the pump device 1 according to the first embodiment. It is explanatory drawing which exaggerates and shows the state shifted to the direction which cross | intersects the axis line L direction with respect to. FIG. 7B is an explanatory view exaggeratingly showing that the support shaft 24 is inclined in the pump device 1 according to the first embodiment.

  In the first embodiment, the second shaft support portion 60 is directed, for example, to an angle range indicated by an arrow θ0 in a direction orthogonal to the axis L with respect to the first shaft support portion 82 provided on the first case 11 side. They are staggered. In this embodiment, the second shaft support portion 60 is a direction (from the suction port 3a to the discharge port 4a) in the direction orthogonal to the axis L with respect to the first shaft support portion 82 provided on the first case 11 side ( (X direction). The first shaft support portion 82 and the second shaft support portion 60 are both shaft holes that extend in parallel with the central axis (axis line L) of the vortex chamber 31.

  The fluid pressure in the vortex chamber 31 is high near the discharge port 4a and low near the suction port 3a. Accordingly, when one end of the support shaft 24 is press-fitted and fixed to the first shaft support portion 82 and the other end is inserted and fixed to the second shaft support portion 60, as shown in FIG. The tip of the other side L2 (second case 12 side) in the axis L direction is inclined to the high pressure side (discharge port 4a side) of the vortex chamber 31. At this time, the tilt center Y of the support shaft 24 is the center in the direction of the axis L of the portion that is press-fitted and fixed to the first shaft support portion 82. Since the direction of the center axis of the vortex chamber 31 is the same as the direction of the axis L as in the first embodiment, the center axis L0 of the support shaft 24 is inclined with respect to the center axis (axis L) of the vortex chamber 31. In this embodiment, the second shaft is supported so that the inclination angle θ1 of the central axis L0 of the support shaft 24 with respect to the axis L of the vortex chamber 31 (first vortex chamber 31a, second vortex chamber 31b) is about 0.3 °. The position of the part 60 is determined.

  Since the rotor 23 rotates around the central axis L0 of the support shaft 24, the rotor 23 rotates in a posture inclined about 0.3 degrees in the vortex chamber 31. Thus, when the rotor 23 is disposed at an inclination, a lateral pressure is applied to the rotor 23 by the fluid pressure from the discharge port 4a toward the suction port 3a, and the rotor 23 is urged to one side L1 in the axis L direction. Therefore, the rotor 23 is positioned with reference to the first case.

  Here, the support shaft 24 can be inclined in a direction different from that in FIG. For example, when the second shaft support portion 60 is arranged to be shifted in the direction opposite to the X direction with respect to the first shaft support portion 82, the support shaft 24 is inclined in the opposite direction. The rotor 23 is biased toward the other side L2 in the direction of the axis L by the lateral pressure applied to the rotor 23 when the rotor 23 rotates, and the rotor 23 is positioned with reference to the second case 12. In this case, it is desirable to provide a washer as a thrust bearing on the second case 12 side.

(Function and effect)
As described above, the pump device 1 according to the first embodiment includes the rotor 23 in which the annular blade portion 21 is formed, the support shaft 24 that rotatably supports the rotor 23, and the drive magnet provided in the rotor 23. 22 includes a stator 29 having a drive coil 27 that constitutes a magnetic drive mechanism, and a pump case 2 in which a rotor arrangement chamber 20 in which a rotor 23 is arranged is formed. A first shaft support portion 82 that supports one end side and a second shaft support portion 60 that supports the other end side of the support shaft 24 are provided, and the rotor arrangement chamber 20 has an annular shape into which the blade portion 21 is inserted. A flow path forming portion 25 is provided, and the flow path forming portion 25 is provided with an arc-shaped vortex chamber 31 (first vortex flow chamber 31a and second vortex flow chamber 31b). Then, the second shaft support portion 60 is arranged with a shift in the direction from the suction port 3a to the discharge port 4a with respect to the first shaft support portion 82, and a predetermined direction with respect to the axis L direction of the vortex chamber 31 The support shaft 24 is installed in a state inclined to the angle.

  Thus, by tilting the support shaft 24 with respect to the direction of the axis L of the vortex chamber 31, the rotor 23 is caused by lateral pressure (fluid pressure in a direction orthogonal to the direction of the axis L) when the rotor 23 rotates. It is urged to one end side or the other end side of the support shaft 24. For example, as shown in FIG. 7B, the second shaft support portion 60 is arranged on the high pressure side (X direction side) with respect to the first shaft support portion 82, so that the side pressure applied to the rotor 23 causes the low pressure side. The rotor 23 is urged toward the first shaft support portion 82 disposed on the (suction port 3a side). Accordingly, the rotating rotor 23 can always be urged to a predetermined side, and the rotor 23 is always positioned in the case on the predetermined side (the first case 11 in the case of the inclination direction of FIG. 7B). . Therefore, even if the thrust bearing is provided on the first case 11 side and the thrust bearing on the second case 12 side is omitted, rattling in the axial direction of the rotor 23 can be avoided and the positional accuracy of the rotor 23 is improved. be able to. Therefore, it is possible to reduce noise due to contact between the rotor 23 and the pump case 2 without using high-precision parts or increasing the number of parts. Can be suppressed.

  In particular, in the first embodiment, since one end of the support shaft 24 is press-fitted and fixed to the first shaft support portion 82, the radial position accuracy of the support shaft 24 with respect to the first case 11 is improved. In addition, since both the first shaft support portion 82 and the second shaft support portion 60 are shaft holes parallel to the axis L direction, the other end of the support shaft 24 is inserted obliquely with respect to the second shaft support portion 60. Thus, the positional accuracy of the support shaft 24 in the radial direction with respect to the second case is also improved. Therefore, the radial position accuracy of the rotor 23 is high. In addition, since the shaft holes (the first shaft support portion 82 and the second shaft support portion 60) are not formed in consideration of the inclination of the support shaft 24, the first case 11 and the second case 12 can be easily manufactured.

  In the first embodiment, the pump case 2 includes the rotor arrangement chamber 20 between the first case 11 provided with the first shaft support portion 82 and the second case 12 provided with the second shaft support portion 60. In the first case 11, a first case-side seal portion 94 that is opposed to the rotor-side seal portion (end surface 45a) provided on the inner peripheral side of the blade portion 21 is formed on the inner peripheral side of the first vortex chamber 31a. In addition, the first case side seal portion 94 and the first shaft support portion 82 on which the rotor 23 is positioned are configured as an integral member. For this reason, even when the clearance (gap G1) of the first case side seal portion 94 is set small by increasing the positional accuracy of the rotor 23, the contact between the rotor 23 and the first case 11 can be avoided.

  In the first embodiment, the first case-side seal portion 94 having the smallest clearance between the rotor 23 and the first case 11 is provided adjacent to the first vortex chamber 31a. For this reason, the leak of the fluid from the 1st vortex chamber 31a can be suppressed, and the fall of pump efficiency can be suppressed. Further, since the position adjacent to the first vortex chamber 31a is on the outer peripheral side of the rotor 23 and the peripheral speed is high at the time of rotation, the noise generated when the rotor 23 and the first case 11 contact each other is large. Therefore, the effect of suppressing the reduction in pump efficiency due to the fact that the contact between the rotor 23 and the first case 11 can be avoided is great, and the effect of reducing noise is great. Moreover, since the seal part between the rotor 23 and the 2nd case 12 is comprised similarly, the same effect is acquired.

  Further, in the first embodiment, the magnetic center position of the stator 29 and the magnetic center position of the rotor 23 are shifted in the direction of the axis L, and the rotor 23 is fluid pressure during rotation and the direction in which the rotor 23 is biased by the magnetic attractive force. The direction energized by is coincident. For this reason, it can prevent that the rotor 23 rattles at the time of starting, and can reduce the noise at the time of starting. In this regard, in the first embodiment, the stator 29 is separated from the rotor arrangement chamber 20 by the first case 11, and the stator 29 and the support shaft 24 are arranged so as to overlap with each other in the axis L direction. It is easy to displace the magnetic center position of the rotor 23 in the direction of the axis L. Further, when the stator 29 and the support shaft 24 are arranged so as to overlap in the axis L direction, the size of the pump device 1 in the axis L direction can be reduced. Therefore, it is advantageous for reducing the thickness of the pump device 1. The magnetic center position of the stator 29 and the magnetic center position of the rotor 23 may be matched. Even in this case, since the rotor 23 can be urged toward the first case 11 during rotation by the fluid pressure in the pump case 2, a noise reduction effect can be obtained and a decrease in pump efficiency can be suppressed.

  In addition, in the first embodiment, the power supply board 30 that controls the current to the drive coil 27 is disposed so as to overlap the stator 29, and the power supply board 30 is in the direction of the axis L with the first shaft support portion 82 of the first case 11. It is arranged overlapping. By disposing the power supply substrate 30 at this position, the first shaft support portion 82 (shaft hole) can be lengthened by the thickness of the power supply substrate 30. Alternatively, the number of stacked washers 43 can be increased by the thickness of the power supply substrate 30. Therefore, the support shaft 24 can be fixed with high accuracy, and the positional accuracy of the rotor 23 is improved.

  In the first embodiment, the outer diameter of the support shaft 24 is constant, and the portion of the support shaft 24 where the washer 43 is mounted is the same as the portion of the support shaft 24 inserted into the cylindrical bearing portion 41. Is the diameter. Therefore, when adjusting the position of the rotor 23 in the axial direction for clearance adjustment at the seal portion on the inner peripheral side of the first vortex chamber 31a, the thickness of the washer 43 is changed, and a plurality of washers 43 are stacked. It can respond by such methods.

(Embodiment 2)
Next, the biasing force generating means employed in the second embodiment of the present invention will be described. 8A and 8B are explanatory views of the rotor 123 which is a biasing force generating unit according to the second embodiment. FIG. 8A is a perspective view of the rotor 123, and FIG. 8B is a bottom surface viewed from one side L1 in the axis L direction. FIG. 8C is a side view of the rotor 123. The pump device according to the second embodiment includes a rotor 123 having a shape different from that of the rotor 23 according to the first embodiment. In the second embodiment, the first shaft support portion 82 and the second shaft support portion 60 are coaxially arranged, and the straight line passing through the radial center of the first shaft support portion 82 and the second shaft support portion 60 is a pump device. 1 substantially coincides with the axis L. Therefore, in the second embodiment, both ends of the support shaft 24 are fixed to the first shaft support portion 82 and the second shaft support portion 60, so that the axis L of the pump case 2 and the center axis of the support shaft 24 are substantially coincident. The rotor 123 rotates about the axis L. Here, “the axis L of the pump case 2 and the center axis of the support shaft 24 substantially coincide with each other” means that the center axis of the support shaft 24 and the axis L of the pump case 2 have a dimensional error in parts or assembly. Including the state of being slightly tilted within the time error range.

  As shown in FIG. 8, the rotor 123 is provided with an annular projecting portion 145 at the outer peripheral portion of the disk portion 140, and a blade portion 121 is formed at the outer peripheral end of the annular projecting portion 145. The annular projecting portion 145 is formed with an inclined groove 100 extending obliquely from an end surface 145a on one side L1 in the axis L direction to an end surface 145b on the other side L2 in the axis L direction. The inclined groove 100 is a groove having a constant width that is recessed at a certain depth inward in the radial direction. The depth of the groove is deeper than the recesses 46 a and 46 b constituting the blade part 121, and more than the range in which the blade part 121 is provided. It is recessed radially inward. In the rotor 123, a plurality of inclined grooves 100 are dispersedly arranged in the circumferential direction at equal angular intervals, and the blade portions 121 are divided into a plurality of circumferential directions by the inclined grooves 100. In this embodiment, the inclined grooves 100 are provided at four locations. In addition, it can also be provided in 3 places or less or 5 places or more.

  As shown in FIG. 8C, the end surface 145a on the one side L1 in the axis L direction of the annular projecting portion 145 and the end surface 145b on the other side L2 are respectively on one end side in the axis L direction of the inclined groove 100. A first opening 101a that is an opening and a second opening 101b that is an opening on the other end side are provided. The inclined groove 100 includes a bottom surface 102 facing radially outward, and inclined surfaces 103a and 103b constituting a pair of parallel side wall surfaces facing in the groove width direction. The inclined surfaces 103 a and 103 b are surfaces inclined in the circumferential direction of the rotor 123, and the inclined groove 100 forms an inclined flow path that penetrates the rotor 123 in the axis L direction and is inclined in the circumferential direction of the rotor 123. . When the rotor 123 is viewed from one side L1 in the axis L direction, the entire inclined surface 103a overlaps the first opening 101a. In addition, when the rotor 123 is viewed from the other side L2 in the axis L direction, the entire inclined surface 103b overlaps the second opening 101b. In other words, the inclined groove 100 is configured such that the inclined surface 103a and the inclined surface 103b do not overlap when viewed in the direction of the axis L. In this way, when the inclined surfaces 103a and 103b are completely exposed when viewed from the axis L direction, the shape of the inclined groove 100 is formed by a mold that is divided into two in the axis L direction without using a slide mold or the like. it can. Therefore, the rotor 123 can be formed by an inexpensive mold.

  Since the inclined groove 100 overlaps the vortex chamber 31 in the radial direction, the rotor 123 rotates around the axis L, and the first opening 101a faces the first vortex chamber 31a (arc groove 34a) of the first case 11. And when the 2nd opening 101b opposes the 2nd eddy current chamber 31b (arc groove 34b) of a 2nd case, the axial flow which passes along the inclination groove | channel 100 generate | occur | produces. For example, by rotating the rotor 123 in the clockwise direction CW (see FIG. 8A) when facing the one side L1 in the axis L direction, the vortex flow from the suction port 3a to the discharge port 4a is generated in the vortex chamber 31. At this time, fluid flows from the first opening 101a toward the second opening 101b. As described above, when the fluid flows from the one side L1 in the axis L direction toward the other side L2 in the inclined groove 100, the inclined surface 103b is pushed to the one side L1 in the axis L direction by the fluid pressure. Thereby, the rotor 123 is urged | biased to the one side L1 of the axis line L direction. That is, the inclined groove 100 (inclined flow path) functions as an urging force generating means for urging the rotating rotor 123 toward one side in the axis L direction, that is, one end side of the support shaft 24.

  Here, the circumferential opening width D1 of the first opening 101a and the second opening 101b provided at both ends of the inclined groove 100 is the circumferential width of the first arc-shaped seal portion 32a and the second arc-shaped seal portion 32b. It is smaller than D2 (see FIG. 4). When the opening width D1 is larger than the width D2 of the seal portion, when the first arc-shaped seal portion 32a and the first opening 101a overlap, or when the second arc-shaped seal portion 32b and the second opening 101b overlap, The suction port 3a and the discharge port 4a communicate with each other through the inclined groove 100, and the fluid leaks between the suction port 3a and the discharge port 4a without passing through the vortex chamber 31. In this embodiment, by making the opening width D1 smaller than the width D2 of the seal portion, the pump efficiency is prevented from being lowered due to fluid leaking between the suction port 3a and the discharge port 4a.

  Further, since the plurality of inclined grooves 100 are formed in the rotor 123 at equal angular intervals in the circumferential direction, fluid pressure acts on the plurality of inclined surfaces 103b arranged at equal angular intervals in the circumferential direction, and the rotor 123 The moment acting in the direction of tilting is canceled out. Moreover, even if any one of the inclined grooves 100 is blocked by the blocking portion 32 (the first arc-shaped seal portion 32a and the second arc-shaped seal portion 32b) by providing the plurality of inclined grooves 100, Since the fluid flows in the inclined groove 100, the rotating rotor 123 can be constantly urged in the direction of the axis L.

(Function and effect)
As described above, the pump device 1 according to the second embodiment includes the rotor 123 in which the annular blade portion 121 is formed, the support shaft 24 that rotatably supports the rotor 123, and the drive magnet provided in the rotor 123. 22 includes a stator 29 having a drive coil 27 that constitutes a magnetic drive mechanism, and a pump case 2 in which a rotor arrangement chamber 20 in which a rotor 123 is arranged is formed. A first shaft support portion 82 that supports one end side and a second shaft support portion 60 that supports the other end side of the support shaft 24 are provided, and the rotor arrangement chamber 20 has an annular shape into which the blade portion 121 is inserted. A flow path forming portion 25 is provided, and the flow path forming portion 25 is provided with an arc-shaped vortex chamber 31 (first vortex flow chamber 31a and second vortex flow chamber 31b). The rotor 123 has an inclined groove as an urging force generating means for generating a fluid pressure acting in a direction for urging the rotating rotor 123 toward one end side of the support shaft 24 (one side L1 in the direction of the axis L). 100 is provided.

  In the pump device 1 of the second embodiment, since the inclined groove 100 is formed in the rotor 123, the fluid pressure of the fluid flowing through the inclined groove 100 when the rotor 123 rotates acts on the inner wall (inclined surface 103b) of the inclined groove 100, As a result, the rotor 123 is biased toward the one side L <b> 1 in the axis L direction, and the rotor 123 is positioned with respect to the first case 11. For this reason, the rotating rotor 123 can be urged in a predetermined direction, and can be positioned with respect to a predetermined case (first case 11). Therefore, even if the thrust bearing is provided on the first case 11 side and the thrust bearing on the second case 12 side is omitted, rattling in the axis L direction of the rotor 123 can be avoided, and the positional accuracy of the rotor 123 can be improved. Can be increased. Therefore, it is possible to reduce noise due to contact between the rotor 123 and the pump case 2 without using high-precision parts or increasing the number of parts, and to suppress a reduction in pump efficiency due to a decrease in position accuracy of the rotor 123. it can.

  In particular, in the second embodiment, since the inclined groove 100 is provided in the outer peripheral portion where the peripheral speed at the time of rotation of the rotor 123 is the highest, the fluid flowing through the inclined groove 100 has a large flow velocity and acts on the inclined surface 103b. The pressure is great. Therefore, the urging force acting on the rotor 123 is large, and rattling prevention and positioning of the rotor 123 can be performed more effectively. Further, when the liquid is pumped, since the fluid pressure acting on the inner wall (sloped surface 103b) of the tilted groove 100 is larger than when gas is pumped, the urging force acting on the rotor 123 becomes larger. Therefore, rattling and positioning of the rotor 123 can be performed more effectively, and a decrease in pump efficiency can be further reduced.

  In the second embodiment, the pump case 2 includes the rotor arrangement chamber 20 between the first case 11 provided with the first shaft support portion 82 and the second case 12 provided with the second shaft support portion 60. The first case 11 has a first case-side seal portion 94 facing the rotor-side seal portion (end surface 145a) provided on the inner peripheral side of the blade portion 121 on the inner peripheral side of the first vortex chamber 31a. In addition, the first case side seal portion 94 and the first shaft support portion 82 on which the rotor 123 is positioned are configured as an integral member. For this reason, even when the clearance (gap G1) of the first case side seal portion 94 is set small by increasing the positional accuracy of the rotor 123, contact between the rotor 123 and the first case 11 can be avoided.

  In the second embodiment, the first case-side seal portion 94 having the smallest clearance between the rotor 123 and the first case 11 is provided adjacent to the first vortex chamber 31a. For this reason, the leak of the fluid from the 1st vortex chamber 31a can be suppressed, and the fall of pump efficiency can be suppressed. Further, since the position adjacent to the first vortex chamber 31a is on the outer peripheral side of the rotor 123 and the peripheral speed is high during rotation, the noise generated when the rotor 123 and the first case 11 are in contact with each other is large. Therefore, the effect of suppressing the reduction in pump efficiency due to the fact that the contact between the rotor 123 and the first case 11 can be avoided is great, and the effect of reducing noise is great. Further, since the seal portion between the rotor 123 and the second case 12 is configured in the same manner, the same effect can be obtained.

  Furthermore, in the second embodiment, the magnetic center position of the stator 29 and the magnetic center position of the rotor 123 are shifted in the direction of the axis L, and the direction in which the rotor 123 is biased by the magnetic attraction force The direction energized by is coincident. For this reason, it can prevent that the rotor 123 rattles at the time of starting, and can reduce the noise at the time of starting. In this regard, in the first embodiment, the stator 29 is separated from the rotor arrangement chamber 20 by the first case 11, and the stator 29 and the support shaft 24 are arranged so as to overlap when viewed from the radial direction. It is easy to displace the magnetic center position and the magnetic center position of the rotor 123 in the direction of the axis L. Further, when the stator 29 and the support shaft 24 are arranged so as to overlap in the axis L direction, the size of the pump device 1 in the axis L direction can be reduced. Therefore, it is advantageous for reducing the thickness of the pump device 1. The magnetic center position of the stator 29 and the magnetic center position of the rotor 123 may be matched. Even in this case, since the rotor 123 can be biased toward the first case 11 during rotation by the fluid pressure applied to the inclined groove 100, a noise reduction effect can be obtained, and a reduction in pump efficiency can be suppressed.

  In addition, in the second embodiment, the power supply board 30 that controls the current to the drive coil 27 is disposed so as to overlap the stator 29 when viewed in the direction of the axis L, and the power supply board 30 is the first axis of the first case 11. It is arranged so as to overlap with the support portion 82 when viewed from the radial direction. By disposing the power supply substrate 30 at this position, the first shaft support portion 82 (shaft hole) can be lengthened by the thickness of the power supply substrate 30. Alternatively, the number of stacked washers 43 can be increased by the thickness of the power supply substrate 30. Therefore, the support shaft 24 can be fixed with high accuracy, and the positional accuracy of the rotor 123 is improved.

  Further, in the second embodiment, the outer diameter of the support shaft 24 is constant, and the portion of the support shaft 24 where the washer 43 is mounted is the same as the portion of the support shaft 24 inserted into the cylindrical bearing portion 41. Is the diameter. Therefore, when adjusting the axial position of the rotor 123 for adjusting the clearance in the seal portion on the inner peripheral side of the first vortex chamber 31a, the thickness of the washer 43 is changed, and the plurality of washers 43 are arranged in an overlapping manner. It can respond by such methods.

(Embodiment 3)
Next, a pump device according to Embodiment 3 of the present invention will be described. The pump device according to the third embodiment includes a rotor 223 that is partially different in shape from the rotor 123 in the pump device according to the second embodiment, and other configurations are the same as those of the second embodiment. That is, both ends of the support shaft 24 are fixed to the first shaft support portion 82 and the second shaft support portion 60, so that the axis L of the pump case 2 is attached so as to substantially coincide with the center axis of the support shaft 24. The rotor 223 rotates about the axis L. In addition, here, “the axis L of the pump case 2 and the center axis of the support shaft 24 substantially coincide” means that the center axis of the support shaft 24 and the axis L of the pump case 2 have a dimensional error or assembly of parts. Including the state of being slightly tilted within the time error range. 9A and 9B are explanatory views of the rotor 223 which is the urging force generating means of the third embodiment, FIG. 9A is a perspective view of the rotor 223, and FIG. 9B is a cross-sectional view of the rotor 223 (FIG. 9A). 9B is a cross-sectional view of the through hole, FIG. 9D is a bottom view of the through hole viewed from the other side L2 in the direction of the axis L, and FIG. It is the top view of the through hole which looked at one side L1 of the axis line L direction.

  The rotor 223 includes a disk portion 240, a cylindrical bearing portion 41, and a cylindrical portion 42. The cylindrical bearing portion 41 and the cylindrical portion 42 are the same as the corresponding portions of the rotor 23 of the first embodiment. The disk part 240 includes an annular projecting part 45 projecting radially outward from the cylindrical part 42, and the blade part 21 is formed at the outer peripheral end of the annular projecting part 45. The blade portion 21 is provided with recesses 46a and 46b, partition plates 47, and ribs 48 on the entire circumference. The annular projecting portion 45 and the blade portion 21 are formed in the same manner as in the case of the rotor 23 of the first embodiment.

  The disc portion 240 is formed with an annular projecting portion 241 that projects radially inward from the cylindrical portion 42 to the other side L2 in the axis L direction with respect to the annular projecting portion 45. A plurality of through holes 110 are formed in the annular projecting portion 241 at equal angular intervals in the circumferential direction. The cross-sectional shape of the through hole 110 is a rectangle. As shown in FIGS. 9B and 9C, the end surface 241a on the one side L1 in the direction of the axis L of the annular protrusion 241 and the end surface 241b on the other side L2 are respectively open on one end side of the through hole 110. A first opening 111a and a second opening 111b which is an opening on the other end side are provided. The through-hole 110 includes a pair of side wall surfaces 112a and 112b that face each other in the radial direction and a pair of inclined surfaces 113a and 113b that face each other in the circumferential direction. The inclined surfaces 113a and 113b are surfaces inclined in the circumferential direction of the rotor 223, and the through hole 110 forms an inclined flow path that penetrates the rotor 223 in the axis L direction and is inclined in the circumferential direction of the rotor 223. .

  As shown in FIG. 9D, when the rotor 223 is viewed facing the other side L2 in the axis L direction, the entire inclined surface 113a overlaps the first opening 111a. Further, as shown in FIG. 9E, when the rotor 223 is viewed facing the one side L1 in the axis L direction, the entire inclined surface 113b overlaps the second opening 111b. In other words, the through hole 110 has a configuration in which the inclined surface 113a and the inclined surface 113b do not overlap each other when viewed in the axis L direction, and the inclined surfaces 113a and 113b extend from the axis L direction as in the inclined groove 100 of the first embodiment. Fully exposed to see. Therefore, it can be molded by a mold that is divided into two in the direction of the axis L.

  An end surface 241 a of the annular projecting portion 241 faces the front end surface of the inner annular projecting portion 90 provided in the first case 11. Further, the end surface 241 b of the annular protrusion 241 faces the bottom surface of the annular recess 64 provided in the second case 12. The fluid leaking from the vortex chamber 31 flows through the gap between the annular protrusion 241 and the first case 11 and the gap between the annular protrusion 241 and the second case 12. Therefore, when the rotor 223 rotates, an axial flow passing through the through hole 110 is generated.

  For example, when the rotor 223 is rotated in the clockwise direction CW (see FIG. 9A) when facing the one side L1 in the axis L direction, the fluid flows from the first opening 111a toward the second opening 111b. At this time, the inclined surface 113b is pushed to the one side L1 in the axis L direction by the fluid pressure, so that the rotor 223 is biased to the one side L1 in the axis L direction. That is, the through hole 110 (inclined flow path) functions as a biasing force generator that biases the rotating rotor 223 toward one side in the direction of the axis L, that is, one end of the support shaft 24. Since the through hole 110 penetrates the rotor 223 on the inner peripheral side with respect to the blade portion 21, a part of the blade portion 21 in the circumferential direction is lost as in the case where the inclined groove 100 of the second embodiment is provided. The partition plate 47 can be provided all around. Therefore, there is an advantage that the pump efficiency is not lowered due to the lack of the partition plate 47.

  Since the through-holes 110 are formed at equal angular intervals in the circumferential direction, similar to the inclined grooves 100 of the second embodiment, fluid pressure acts on a plurality of inclined surfaces 113b arranged at equal angular intervals in the circumferential direction. The moment acting in the direction in which the rotor 223 tilts is canceled out.

  Further, the through hole 110 penetrates the rotor 223 on the inner peripheral side with respect to the blade part 21, and the rotor side seal part (first case side seal part 94, second case side seal) that seals the vortex chamber 31 from the inside. (Part facing the portion 67) is provided on the inner peripheral side. Since the second case-side seal portion 67 is provided with a short-circuit groove 67a, when a liquid such as water is pumped as a fluid, the second vortex flow is the same as in the through hole 40b of the first and second embodiments. The air that has entered the chamber 31b is guided to the inner peripheral side through the short-circuit groove 67a of the second case side seal portion 67, and is sent to the discharge port 4a side through the through hole 110 provided in the disk portion 240 of the rotor 223. The pump case 2 can be discharged.

  As described above, when the rotor 223 of the third embodiment is used instead of the rotor 123 of the second embodiment, the rotating rotor 223 can be biased toward one end side of the support shaft 24. Therefore, rattling in the axis L direction of the rotor 223 can be avoided during rotation, and the positional accuracy of the rotor 223 can be improved. Therefore, noise due to contact between the rotor 223 and the pump case 2 can be reduced, and reduction in pump efficiency due to a decrease in position accuracy of the rotor 223 can be suppressed.

(Other embodiments)
(1) In the first to third embodiments, the present invention is applied to a shaft-fixed pump device. However, the present invention can also be applied to a shaft-rotating pump device. In the case of a shaft rotation type pump device, instead of the support shaft 24 of each of the above embodiments, a rotation shaft (rotation center shaft) that rotates integrally with the rotor 23 (123, 223) is provided. And the bearing part which supports a rotating shaft rotatably is provided in the 1st shaft support part 82 and the 2nd shaft support part 60. As shown in FIG. Even in such a configuration, the urging force generating means of the first to third embodiments can generate the fluid pressure acting on the rotor 23 (123, 223), and the rotor 23 (123, 223) together with the central axis. ) To increase the positional accuracy of the rotor 23 (123, 223). Therefore, noise due to contact between the rotor 23 (123, 223) and the pump case 2 can be reduced without using high-precision parts or increasing the number of parts, and the position of the rotor 23 (123, 223) can be reduced. A decrease in pump efficiency due to a decrease in accuracy can be suppressed.

  (2) In the pump device 1 of the first embodiment, the rotor 123 of the second embodiment or the rotor 223 of the third embodiment may be used. In this case, in addition to the urging force generated by inclining the support shaft 24, the urging force generated by providing the inclined groove 100 or the through hole 110 is added, so that the rotor can be urged with a larger force.

  (3) The urging force generating means is not limited to the configuration as in the first to third embodiments, and various dynamic pressure generating means may be provided in at least one of the pump case and the rotor. For example, in the second embodiment, the rotor 123 is provided with dynamic pressure generating means (inclined surfaces 103a and 103b), and in the third embodiment, the rotor 223 is provided with dynamic pressure generating means (inclined surfaces 113a and 113b). Dynamic pressure generating means such as an inclined surface may be provided in a portion constituting the rotor arrangement chamber 20.

DESCRIPTION OF SYMBOLS 1 Pump apparatus 1A Pump apparatus 2 Pump case 2a 1st end surface 2b 2nd end surface 2c 1st side surface 2d 2nd side surface 2e 3rd side surface 2f 4th side surface 2k Inclined surface 3 Intake pipe 3a Inlet port 4 Outlet tube 4a Outlet port 5 Lead Wire 6 Wiring extraction part 6a Fixing member 7 Connector 8 Hook 9 Mounting hole 10a Through hole 10b Screw hole 11 First case 12 Second case 13 Anti-rotation mechanism 13a Anti-rotation protrusion 13b Anti-rotation recess 14 Case fixing part 14A First protrusion 14B 2nd protrusion part 16 Sealant 20 Rotor arrangement chamber 21 Blade part 22 Drive magnet 23 Rotor 24 Support shaft 24a Support shaft side guide surface 25 Flow path forming part 26 O-ring 27 Drive coil 28 Stator core 29 Stator 30 Feeding board 30a Opening Portion 31 vortex chamber 31a first vortex chamber 31b second vortex chamber 32 sealed portion 32a first arc-shaped seal portion 32b Second arc-shaped seal portions 34a, 34b Arc groove 40 Disc portion 40a Annular protrusion 40b Through hole 41 Cylindrical bearing portion 41a Center hole 42 Cylindrical portion 43 Washer 44 Yoke 45 Annular overhanging portions 45a, 45b End surfaces 46a, 46b Recessed portion 47 Partition plate 48 Rib 50 Annular portion 51 Salient pole 52 Plate-shaped core piece 53 Inner recess 60 Second shaft support portion 60a Shaft hole side guide surface 61 Bottom plate portion 62 Side wall portion 63 Circular recess 64 Annular recess 65 Inner annular protrusion 66 Outer annular Protruding portion 66a End surface 67 Second case side seal portion 67a Short-circuit groove 68 Annular step portion 68a Annular end surface 68b Inner peripheral surface 80 Central projecting portion 81 Circular recess 81a Bottom surface 82 First shaft support portion 83 Stator storage chamber 86 Outer peripheral wall 89 Cylindrical portion 90 inner annular protrusion 91 outer annular protrusion 91a end face 92 annular recess 93 overhanging portion 94 first case side Seal portion 95 Outer peripheral surface 96 Radial protrusion 96a Annular end surface 96b Outer peripheral surface 100 Inclined groove 101a First opening 101b Second opening 102 Bottom surface 103a, 103b Inclined surface 110 Through hole 111a First opening 111b Second opening 112a, 112b Side wall surface 113a, 113b Inclined surface 121 Blade portion 123 Rotor 145 Annular overhanging portion 145a, 145b End surface 223 Rotor 240 Disc portion 241 Annular protrusions 241a, 241b End surface D1 Opening width D2 Width of seal portion G1, G2 Gap L Axis L0 Center axis Y Inclination Center θ1 Tilt angle

Claims (17)

A rotor provided with a plurality of blade portions in a circumferential direction at an outer peripheral side end portion;
A magnet that is held by the rotor and a stator that forms a magnetic drive mechanism;
A rotor arrangement chamber in which the rotor is arranged, a vortex chamber that extends in a circular arc shape in the circumferential direction on the outer peripheral side of the rotor arrangement chamber, and has both ends communicating with the suction port and the discharge port, respectively, A pump case including a first shaft support portion that supports one end and a second shaft support portion that supports the other end of the rotation center shaft;
An urging force generating means for generating a fluid pressure for urging the rotor toward one side of a rotation center axis of the rotor when the rotor rotates;
A pump apparatus comprising: The pump case includes a first case provided with the first shaft support portion, a second case provided with the second shaft support portion and constituting the rotor arrangement chamber between the first case, Have
The first case is opposed to a first rotor side seal portion provided at a portion radially inward of the blade portion on one side of the rotation center axis of the rotor in the rotation center axis direction. The pump device according to claim 1, wherein a first case side seal portion is formed. The first case side seal portion is adjacent to the vortex chamber on the radially inner side,
3. The pump device according to claim 2, wherein a clearance between the first case and the rotor is minimum in the rotor-side seal portion and the first case-side seal portion. The stator is disposed at a position overlapping the rotation center axis when viewed from the radial direction,
4. The magnetic center of the stator in the rotation center axis direction is deviated toward a biasing direction side of the rotor by the biasing force generating means with respect to the magnetic center of the rotor. The pump device according to any one of the items. The first case includes a partition wall that separates the stator from the rotor arrangement chamber.
A bottomed tube portion in which the first shaft support portion is formed in the partition wall portion is provided,
4. The pump device according to claim 1, wherein the power supply substrate to the stator is disposed on a radially outer side of the cylindrical portion. 5. The rotation center axis is a spindle whose both ends are fixed to the first shaft support portion and the second shaft support portion,
An annular thrust bearing fitted to the support shaft is disposed between one end surface of the rotation center axis of the cylindrical bearing portion that fits to the support shaft in the rotor and the first case,
The pump device according to any one of claims 1 to 5, wherein a portion of the support shaft into which the thrust bearing fits and a portion into which the cylindrical bearing portion fits have the same diameter.   The urging force generating means is configured by the first shaft support portion and the second shaft support portion being displaced in a direction intersecting with a central axis of the vortex chamber. Item 7. The pump device according to any one of Items 1 to 6.   The urging force generating means is configured such that the second shaft support portion is displaced in a direction from the suction port toward the discharge port with respect to the first shaft support portion. 8. The pump device according to 7. The first shaft support portion and the second shaft support portion are shaft holes that are recessed parallel to the central axis of the vortex chamber,
The pump device according to claim 7 or 8, wherein the rotation center shaft is press-fitted and fixed to the first shaft support portion.   The pump device according to any one of claims 1 to 6, wherein the biasing force generating means is an inclined flow path formed in the rotor with an inclined surface inclined in a circumferential direction.   The pump device according to claim 10, wherein the inclined channels are arranged at equiangular intervals at a plurality of locations in the circumferential direction.   The inclined flow path includes a first opening that opens at one end surface of the rotation center axis of the rotor, and a second opening that opens at the other end surface of the rotation center axis of the rotor. The pump device according to claim 10 or 11, characterized in that   The pump device according to claim 12, wherein the entire inclined surface overlaps one of the first opening and the second opening when viewed from the rotation center axis direction. The first opening and the second opening are formed at radial positions overlapping the vortex chamber in the rotor when viewed from the rotation center axis direction,
The circumferential opening width of the first opening and the second opening is smaller than the circumferential width of the arc-shaped seal portion in which the vortex chamber is not formed in the circumferential direction. The pump device described in 1.   The pump device according to any one of claims 10 to 14, wherein the inclined flow path is formed in a groove shape at the outer peripheral side end of the rotor.   The pump device according to any one of claims 10 to 13, wherein the inclined channel is a through channel that penetrates the rotor radially inward from the blade portion. The through channel is formed radially inward of a seal portion provided radially inward of the blade portion between the rotor and the pump case,
The pump device according to claim 16, wherein a short-circuit groove is formed in the seal portion to communicate the radially inner side and the radially outer side of the seal portion.

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