pump

Abstract

To restrain vibration and noise from occurring.SOLUTION: A pump 1 comprises a pump case 2, a rotating shaft 6, a bearing 7, an impeller 9, a driving part 3, a receiving plate 100, and a positioning member 200. The pump case 2 forms at least a portion of a pump chamber Sp3. One end of the rotating shaft 6 is inserted into a portion of the pump case 2. The rotating shaft 6 is passed through the bearing 7. The driving part 3 rotates the impeller 9 to make fluid flow. The rotating shaft 6 is passed through the receiving plate 100. The receiving plate 100 is located between the bearing 7 and the portion of the pump case 2, and is in contact with an opposed surface 71 of the bearing 7. The positioning member 200 is located between the receiving plate 100 and the portion of the pump case 2, and defines the position of the receiving plate 100 in an extending direction D1.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] FIELD OF THE DISCLOSURE The present disclosure relates generally to pumps, and more particularly to pumps with impellers. [Background technology]

[0002] Patent document 1 describes a submersible plain bearing pump that includes a shaft fixed by a separation plate and a casing, an impeller having a bearing that rotates around the shaft, and a bearing plate attached to the shaft so as to be positioned between the bearing and the casing shaft support.

[0003] In the submersible plain bearing pump described in Patent Document 1, the impeller rotates around the shaft with the end of the bearing in contact with the surface of the bearing plate. Also, when the impeller rotates, the bearing plate comes into contact with the casing shaft support. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2006-37825 Summary of the Invention [Problem to be solved by the invention]

[0005] When assembling the shaft to the separator plate and casing (pump case), the shaft may be tilted relative to the casing. If the shaft is tilted relative to the casing, the bearing plate may come into contact with the casing shaft support when the impeller rotates (when the pump is operating), causing the bearing plate to tilt relative to the shaft and bearing. If the bearing plate is tilted relative to the shaft and bearing, this may increase vibration and noise when the pump is operating.

[0006] The present disclosure has been made in consideration of the above-mentioned circumstances, and aims to provide a pump that is capable of suppressing the generation of vibrations and noise during operation of the pump. [Means for solving the problem]

[0007] A pump according to one aspect of the present disclosure includes a pump case, a rotating shaft, a bearing, an impeller, a drive unit, a backing plate, and a positioning member. The pump case forms at least a portion of a pump chamber. The rotating shaft is located inside the pump chamber, and one end is inserted into a portion of the pump case. The rotating shaft passes through the bearing. The impeller has a fluid flow path. The drive unit rotates the impeller around the rotating shaft as a rotation center to cause the fluid to flow. The rotating shaft passes through the backing plate. The backing plate is located between the bearing and the portion of the pump case in the extension direction of the rotating shaft and contacts the opposing surface of the bearing. The positioning member is located between the backing plate and the portion of the pump case in the extension direction and determines the position of the backing plate in the extension direction. The part of the pump case is a cylindrical portion formed into a bottomed cylindrical shape so that the one end of the rotary shaft can be inserted therein. A gap is formed between the positioning member and the cylindrical portion. The positioning member is tiltable relative to the cylindrical portion. [Effects of the Invention]

[0008] According to the present disclosure, it is possible to provide a pump that is capable of suppressing the generation of vibration and noise. [Brief explanation of the drawings]

[0009] [Figure 1] FIG. 1 is a cross-sectional view of a pump according to a first embodiment. [Figure 2] FIG. 2 is an enlarged cross-sectional view of a main part of the pump according to the above embodiment. [Figure 3] FIG. 3 is a perspective view of a positioning member of the pump according to the first embodiment. [Figure 4] FIG. 4 is a perspective view of the positioning member according to the first embodiment, seen from a different angle. [Figure 5] FIG. 5 is a schematic view of the main part of the pump according to the above embodiment. [Figure 6] FIG. 6 is a perspective view of a main part of the impeller of the pump according to the same embodiment. [Figure 7] FIG. 7 is a plan view of a main part of the impeller according to the same. [Figure 8] FIG. 8 is a cross-sectional view of a main part of the impeller according to the same. [Figure 9] FIG. 9 is a graph showing the relationship between the cross-sectional area and the position in the flow path of the impeller according to the embodiment. [Figure 10] FIG. 10 is a perspective view of a positioning member of a pump according to a first modified example. [Figure 11] FIG. 11 is a schematic diagram of a main part of a pump according to a second modified example. [Figure 12] FIG. 12 is a perspective view of a positioning member of the pump according to the first embodiment. [Figure 13] FIG. 13 is a perspective view of the positioning member according to the first embodiment, seen from a different angle. [Figure 14] FIG. 14 is a perspective view of a positioning member of a pump according to a third modified example. [Figure 15] FIG. 15 is a schematic view of the main part of the pump according to the same embodiment. [Figure 16] FIG. 16 is a schematic view of a main part of a pump according to the second embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0010] Preferred embodiments of the present disclosure will be described in detail below with reference to the drawings. Elements common to the embodiments described below are designated by the same reference numerals, and redundant descriptions of the common elements will be omitted. Each of the following embodiments is merely one of various embodiments of the present disclosure. Various modifications can be made to each embodiment depending on the design, etc., as long as the object of the present disclosure can be achieved.

[0011] The drawings described in this disclosure are schematic diagrams, and the ratios of the sizes and thicknesses of the components in the drawings do not necessarily reflect the actual dimensional ratios. Note that the arrows indicating the directions are merely examples and are not intended to define the directions in which the pump 1 should be used. Furthermore, the arrows indicating the directions in the drawings are merely shown for explanatory purposes and have no substance.

[0012] In this disclosure, "orthogonal (perpendicular)" does not only mean that the angle between two objects is exactly 90°, but also means that the angle between two objects is approximately perpendicular within a certain margin of error. In other words, the angle between two orthogonal objects falls within a certain margin of error (for example, 10° or less) from 90°.

[0013] In the following explanation, when illustrating values ​​such as distance and area, "less than" may also mean "less than." In other words, when comparing two values, whether or not the two values ​​are equal can be arbitrarily changed depending on the setting of the reference value, etc., so there is no technical difference between "less than" and "less than." Similarly, "greater than" may also mean "exceeding."

[0014] (Embodiment 1) (1) Overview First, an overview of a pump 1 according to a first embodiment will be described with reference to FIGS. 1, 2, and 6. FIG.

[0015] As shown in FIG. 1, the pump 1 includes a pump case 2, a drive unit 3, a rotary shaft 6, a bearing 7, an impeller 9, a backing plate 100, and a positioning member 200.

[0016] The pump case 2 forms at least a part of the pump chamber Sp3. The pump case 2 of the first embodiment also has a cylindrical portion 21 into which one end (first end portion 61) of the rotary shaft 6 is inserted.

[0017] The rotating shaft 6 is located inside the pump chamber Sp3. A first end 61 of the rotating shaft 6 is inserted into a cylindrical portion 21 that is a part of the pump case 2. More specifically, the first end 61 of the rotating shaft 6 in the first embodiment is inserted into the cylindrical portion 21 via a positioning member 200.

[0018] The bearing 7 is a cylindrical member through which the rotary shaft 6 passes. The bearing 7 rotates around the rotary shaft 6.

[0019] The impeller 9 has a flow path 96 (see FIG. 6) through which a fluid such as a liquid flows.

[0020] The driver 3 rotates the impeller 9 to cause the fluid to flow. Specifically, the driver 3 changes the magnetic field to rotate the impeller 9 around the rotation axis 6. When the driver 3 rotates the impeller 9, the pump 1 sucks liquid such as water from the suction port 22 into the pump chamber Sp3 and discharges the liquid from the discharge port 24 to the outside of the pump 1.

[0021] As shown in Figure 2, the backing plate 100 is located between the bearing 7 and the cylindrical portion 21, which is part of the pump case 2, in the extension direction D1 of the axis Ax1 (see Figure 1) of the rotating shaft 6. The rotating shaft 6 passes through the backing plate 100. The backing plate 100 comes into contact with the opposing surface 71 of the bearing 7 when the impeller 9 rotates.

[0022] The positioning member 200 is located in the extension direction D1 between the backing plate 100 and the cylindrical portion 21, which is part of the pump case 2. The positioning member 200 defines the position of the backing plate 100 in the extension direction D1.

[0023] The positioning member 200 determines the position of the backing plate 100 in the extension direction D1, thereby preventing contact between the backing plate 100 and the tubular portion 21. For example, even if the rotating shaft 6 is attached at an angle with respect to the pump case 2 (tubular portion 21), preventing contact between the backing plate 100 and the tubular portion 21 can prevent the backing plate 100 from tilting with respect to the rotating shaft 6. Preventing the backing plate 100 from tilting with respect to the rotating shaft 6 stabilizes contact between the opposing surface 71 of the bearing 7 and the rear surface 101 of the backing plate 100, thereby reducing vibration and noise during operation of the pump 1.

[0024] (2)Details The pump 1 according to the first embodiment will be described in detail below with reference to Figures 1 to 9. In the following description, the extension direction D1 of the axis Ax1 of the rotating shaft 6 is defined as the "front-rear direction." Furthermore, the direction from the rotating shaft 6 toward the cylindrical portion 21 of the pump case 2 is defined as the "front," and the direction from the cylindrical portion 21 toward the rotating shaft 6 is defined as the "rear."

[0025] The pump 1 is a pump used, for example, underwater. As shown in Fig. 1, the pump 1 includes a pump case 2, a drive unit 3, a rotating shaft 6, a bearing 7, a rotor unit 8, an impeller 9, a backing plate 100, a positioning member 200, an elastic member 300, and a plate 400.

[0026] (2.1) Pump case The pump case 2 has a cylindrical portion 21, a suction portion 22, a base portion 23, and a discharge portion 24.

[0027] The base 23 has a cylindrical shape with a bottom. The base 23 forms a first space Sp1 that houses the impeller 9. The first space Sp1 is at least a part of the pump chamber Sp3. In other words, the base 23 (pump case 2) forms at least a part of the pump chamber Sp3. The base 23 has a first opening 231 and a second opening 232.

[0028] The first opening 231 is formed in the bottom of the base 23 along the extension direction D1 (front-rear direction) of the rotating shaft 6. The shape of the first opening 231 in the first embodiment is circular in a plan view along the extension direction D1. However, the shape of the first opening 231 is not limited to a circular shape, and the shape of the first opening 231 may be, for example, a polygonal shape.

[0029] The second opening 232 is formed on the side periphery of the base 23. The shape of the second opening 232 is circular in a plan view along the radial direction D2. However, the shape of the second opening 232 is not limited to a circular shape and may be, for example, a polygonal shape. The radial direction D2 is a direction perpendicular to the extension direction D1 of the rotating shaft 6 and is a direction along the diameter of an imaginary circle centered on the axis Ax1 of the rotating shaft 6.

[0030] Suction portion 22 protrudes forward from the edge of first opening 231 of base portion 23. Suction portion 22 is cylindrical in shape. However, the shape of suction portion 22 is not limited to a cylindrical shape and may be, for example, a tubular shape with a polygonal cross section. When impeller 9 is operating, suction portion 22 draws in liquid such as water from outside pump 1.

[0031] The discharge portion 24 protrudes from the side periphery of the base portion 23. The shape of the discharge portion 24 in the first embodiment is cylindrical. However, the shape of the discharge portion 24 is not limited to cylindrical, and may be, for example, a tubular shape with a polygonal cross section. The internal space of the discharge portion 24 and the first space Sp1 are connected through the second opening 232. When the impeller 9 is operating, the discharge portion 24 discharges the liquid in the pump chamber Sp3 (first space Sp1) to the outside of the pump 1.

[0032] The tubular portion 21 is supported by the base portion 23 so as to be located forward of the rotary shaft 6 in the extension direction D1 and inside an inner edge portion 921 of the rear shroud 92 in the radial direction D2. The tubular portion 21 is formed in a cylindrical shape with a bottom. As shown in FIG. 2 , the tubular portion 21 has a bottom 211 and a side peripheral portion 212. The bottom 211 is circular. The side peripheral portion 212 protrudes rearward from the edge of the bottom 211. The side peripheral portion 212 is cylindrical. Note that the shape of the tubular portion 21 is not limited to a cylindrical shape with a bottom, and may be a rectangular cylindrical shape with a bottom, an elliptical cylindrical shape with a bottom, or a cylindrical shape with a bottom in which a portion of the side peripheral portion 212 is missing. The tubular portion 21, which is a part of the pump case 2, is formed so that the first end portion 61 (one end) of the rotary shaft 6 is inserted therein.

[0033] (2.2) Drive unit 1 rotates an impeller 9 about a rotation axis 6 as a rotation center to cause a liquid to flow. The drive unit 3 has a molded portion 4 and a separation plate 5.

[0034] (2.2.1) Mold section The molded section 4 is formed by resin-molding each part for driving the rotor section 8. The molded section 4 has a cylindrical shape with a bottom. The molded section 4 forms a second space Sp2 that houses the rotor section 8. The second space Sp2 is at least a part of the pump chamber Sp3. In other words, the molded section 4 (drive section 3) forms at least a part of the pump chamber Sp3.

[0035] The molded part 4 has a bottom part 45 and a peripheral side part 46. The bottom part 45 is circular in shape. The peripheral side part 46 protrudes forward from the edge of the bottom part 45. The peripheral side part 46 is cylindrical in shape. However, the shape of the bottom part 45 is not limited to a circular shape and may be, for example, a polygonal shape. The shape of the peripheral side part 46 is not limited to a cylindrical shape and may be, for example, a rectangular tube shape.

[0036] The molded part 4 has a stator having a plurality of teeth 41 and a plurality of coils 42, a control part 43, and a connection part 44. In the following description, each of the plurality of teeth 41 may be referred to as a "tooth 41." Also, each of the plurality of coils 42 may be referred to as a "coil 42."

[0037] The connection portion 44 is exposed from the bottom portion 45 of the molded portion 4. The connection portion 44 electrically connects the control portion 43 and the plurality of coils 42 to an external device such as a power supply that supplies power to the control portion 43 and the plurality of coils 42.

[0038] The teeth 41 and the coils 42 are provided on a peripheral side portion 46. The coils 42 are wound around the teeth 41. When a current is applied to the coils 42, a magnetic field is generated.

[0039] The control unit 43 is provided on the bottom portion 45. The control unit 43 changes the magnetic field by controlling the energization of the plurality of coils 42. More specifically, the control unit 43 changes the magnetic field by controlling the energization of the plurality of coils 42 so that the rotor portion 8 rotates.

[0040] (2.2.2) Separation plate The separation plate 5 covers the front surface of the bottom 45 of the molded section 4 and the front surface and inner circumferential surface of the side circumferential section 46. The separation plate 5 is disposed between the molded section 4 and the pump chamber Sp3. In other words, the separation plate 5 separates the molded section 4 from the pump chamber Sp3. By covering the front surface of the bottom 45 of the molded section 4 and the front surface and inner circumferential surface of the side circumferential section 46, the separation plate 5 prevents water from entering the inside of the molded section 4 from the pump chamber Sp3.

[0041] The separation plate 5 has a bottom portion 51, a peripheral side portion 52, a flange portion 53, and a tubular portion 54. The bottom portion 51 covers the front surface of the bottom portion 45 of the molded portion 4. The bottom portion 51 is circular in shape. The peripheral side portion 52 protrudes forward from the edge of the bottom portion 51. The peripheral side portion 52 is cylindrical in shape. The peripheral side portion 52 covers the inner circumferential surface of the peripheral side portion 46 of the molded portion 4. The flange portion 53 protrudes from the front end of the peripheral side portion 52 along the radial direction D2. The flange portion 53 is annular in shape. The flange portion 53 covers the front surface of the peripheral side portion 46 of the molded portion 4.

[0042] The tubular portion 54 protrudes forward from the center of the bottom portion 51. The tubular portion 54 has a cylindrical shape. A second end portion 62 (described later) of the rotary shaft 6 is inserted into the tubular portion 54.

[0043] (2.3) Rotation axis The rotating shaft 6 is located inside the pump chamber Sp3. The rotating shaft 6 is made of, for example, ceramic. As shown in FIG. 2, the rotating shaft 6 has a base 60, a first end 61, and a second end 62.

[0044] The base 60 has a cylindrical shape. The base 60 may have a cylindrical shape. The axis Ax1 of the rotating shaft 6 is the center of the base 60.

[0045] The first end 61 protrudes forward from the front end of the base 60. The first end 61 has a cylindrical shape with a semicircular cross section. The first end 61 may have a polygonal or elliptical cylindrical shape. The first end 61 is one end of the rotating shaft 6, and is inserted into the tubular portion 21, which is a part of the pump case 2. The first end 61 of the first embodiment is inserted into the tubular portion 21, which is a part of the pump case 2, via a positioning member 200.

[0046] The second end 62 protrudes rearward from the rear end of the base 60. The second end 62 has a cylindrical shape with a semicircular cross section. The second end 62 may also have a polygonal or elliptical cylindrical shape. The second end 62 is the other end of the rotating shaft 6, and is inserted into the tubular portion 54, which is part of the separation plate 5.

[0047] (2.4) Bearings The bearing 7 is located between the plate 400 and the backing plate 100 in the extension direction D1. The bearing 7 has a cylindrical shape. The rotation shaft 6 passes through the bearing 7. The bearing 7 is configured to be movable between the plate 400 and the backing plate 100 along the extension direction D1.

[0048] The bearing 7 of the first embodiment is provided in the rotor unit 8 so as to operate integrally with the rotor unit 8, and rotates around the base 60 of the rotary shaft 6. The bearing 7 is formed of, for example, a resin mixed with a carbon material such as graphite. The bearing 7 has an opposing surface 71 that faces the backing plate 100 in the extension direction D1. The normal to the opposing surface 71 is aligned with the extension direction D1.

[0049] (2.5) Rotor As shown in FIG. 1, the rotor unit 8 has a base portion 81, a magnet 82 having a plurality of magnetic poles, a first connecting portion 83, and a second connecting portion 84.

[0050] The base 81 has a cylindrical shape. The base 81 holds a magnet 82. The magnet 82 is a permanent magnet such as a neodymium magnet.

[0051] The first connecting portion 83 has a cylindrical shape. In a plan view along the extension direction D1, the first connecting portion 83 surrounds the receiving plate 100, the positioning member 200, and the tubular portion 21 of the pump case 2. A portion of the outer peripheral surface of the first connecting portion 83 is connected to the inner peripheral surface of the front end of the base portion 81. The rear end of the first connecting portion 83 is located rearward of the front end of the base portion 81, and the front end of the first connecting portion 83 is located forward of the front end of the base portion 81. The front end of the first connecting portion 83 is connected to an inner edge portion 921 of the rear shroud 92. In other words, the first connecting portion 83 protrudes rearward from the inner edge portion 921 of the rear shroud 92.

[0052] The second connecting portion 84 protrudes rearward from the inner peripheral surface of the rear end of the first connecting portion 83. The second connecting portion 84 is cylindrical in shape. The diameter of the inner peripheral surface of the second connecting portion 84 roughly matches the diameter of the outer peripheral surface of the bearing 7. The second connecting portion 84 and the bearing 7 are connected. Because the second connecting portion 84 and the bearing 7 are connected, the rotor portion 8 and the bearing 7 operate as a single unit.

[0053] The rotor section 8 rotates due to the interaction between a magnetic field generated by current flowing through the multiple coils 42 of the stator and a magnetic field generated by the magnets 82 of the rotor section 8.

[0054] (2.6) Receiving plate As shown in FIG. 2, the backing plate 100 is located in front of the bearing 7. More specifically, the backing plate 100 is located between the bearing 7 and the cylindrical portion 21, which is a part of the pump case 2, in the extension direction D1. More specifically, the backing plate 100 is located between the bearing 7 and the positioning member 200 in the extension direction D1. The first end 61 of the rotating shaft 6 is passed through a hole 103 in the backing plate 100. The hole 103 is semicircular in shape. The hole 103 is configured so that the backing plate 100 does not rotate relative to the rotating shaft 6 (first end 61) when the first end 61 of the rotating shaft 6 is passed through the hole 103. The backing plate 100 is made of, for example, ceramic. The backing plate 100 is configured to be movable between the bearing 7 and the positioning member 200 along the extension direction D1.

[0055] The backing plate 100 is a circular (annular) flat plate having a hole 103. A front surface 102 and a rear surface 101 of the backing plate 100 are parallel to each other, and the normals of the front surface 102 and the rear surface 101 are along the extension direction D1. The rear surface 101 of the backing plate 100 comes into contact with the opposing surface 71 of the bearing 7 when the impeller 9 rotates.

[0056] (2.7) Board The plate 400 is located behind the bearing 7. More specifically, the plate 400 is located between the bearing 7 and the cylindrical portion 54, which is a part of the separation plate 5, in the extension direction D1. The second end 62 of the rotating shaft 6 passes through a hole 401 in the plate 400. The hole 401 has a semicircular shape. The hole 401 is configured so that the plate 400 does not rotate with respect to the rotating shaft 6 (second end 62) when the second end 62 of the rotating shaft 6 is passed through the hole 401. The plate 400 is formed of, for example, ceramic.

[0057] (2.8) Positioning member The positioning member 200 is located in front of the backing plate 100. More specifically, the positioning member 200 is located between the backing plate 100 and a cylindrical portion 21 that is a part of the pump case 2 in the extension direction D1. The positioning member 200 of the first embodiment is formed in a cylindrical shape with a bottom. As shown in FIGS. 3 and 4 , the positioning member 200 of the first embodiment has a side peripheral portion 201, a rear surface 202, a circular bottom portion 203, and an edge portion 204.

[0058] The edge portion 204 protrudes forward from the edge of the bottom portion 203. The edge portion 204 has a cylindrical shape. In a plan view along the extension direction D1, the edge portion 204 surrounds the elastic member 300 (see FIG. 2).

[0059] The side circumferential portion 201 protrudes rearward from the edge of the bottom portion 203. The side circumferential portion 201 has a cylindrical shape with a D-shaped cross section. As shown in FIG. 4 , the inner circumferential surface of the side circumferential portion 201 has a flat surface 205 and a circumferential surface 206. In the pump 1 of the first embodiment, the first end 61 of the rotating shaft 6 is inserted into the inner circumferential surface of the side circumferential portion 201, and the inner circumferential surface of the side circumferential portion 201 and the semicircular outer circumferential surface of the first end 61 are fitted together. In other words, the positioning member 200 of the first embodiment covers the first end 61 (one end) of the rotating shaft 6. The inner circumferential surface of the side circumferential portion 201 is fitted together with the outer circumferential surface of the first end 61, thereby fixing the positioning member 200 to the rotating shaft 6. By fitting the first end 61 of the rotating shaft 6 into the positioning member 200, the positioning member 200 can be fixed to the rotating shaft 6 more firmly.

[0060] As shown in Figure 2, the rear surface 202 is a flat portion at the rear end of the side peripheral portion 201. A normal to the rear surface 202 is along the extension direction D1. The rear surface 202 comes into contact with the front surface 102 of the backing plate 100 when the pump 1 is operating. In other words, when the pump 1 is operating, the positioning member 200 determines the position of the backing plate 100 in the extension direction D1.

[0061] The positioning member 200 determines the position of the backing plate 100 in the extension direction D1, thereby making it possible to prevent contact between the backing plate 100 and the tubular portion 21. For example, even if the rotating shaft 6 is attached at an angle with respect to the pump case 2 (tubular portion 21), preventing contact between the backing plate 100 and the tubular portion 21 makes it possible to prevent the backing plate 100 from tilting with respect to the rotating shaft 6. By preventing the backing plate 100 from tilting with respect to the rotating shaft 6, contact between the opposing surface 71 of the bearing 7 and the rear surface 101 of the backing plate 100 can be stabilized, making it possible to suppress the generation of vibrations and noise when the pump 1 is operating.

[0062] Furthermore, when the pump 1 is operating, the rear surface 202 of the positioning member 200 comes into contact with the front surface 102 of the receiving plate 100, whereby the positioning member 200 determines the intersection angle θ1 (see FIG. 5 ) between the flat surface (rear surface 101) of the receiving plate 100 and the rotation shaft 6. For example, the positioning member 200 determines the intersection angle θ1 between the flat surface of the receiving plate 100 and the rotation shaft 6 by preventing the receiving plate 100 from coming into contact with the cylindrical portion 21. The intersection angle θ1 between the flat surface of the receiving plate 100 and the rotation shaft 6, determined by the positioning member 200, is preferably in the range of 85° to 95°. Furthermore, the intersection angle θ1 between the flat surface of the receiving plate 100 and the rotation shaft 6, determined by the positioning member 200, is more preferably in the range of 88° to 92°. By determining the intersection angle θ1 between the rear surface 101 of the receiving plate 100 and the rotation shaft 6 by the positioning member 200, tilting of the receiving plate 100 with respect to the rotation shaft 6 can be further suppressed.

[0063] Furthermore, the intersection angle θ2 (see FIG. 5 ) between the rear surface 202 of the positioning member 200 of embodiment 1 and the rotation shaft 6 is 90° (vertical). That is, the positioning member 200 of embodiment 1 defines the intersection angle θ1 between the flat surface (rear surface 101) of the backing plate 100 and the rotation shaft 6 to 90° (vertical). For example, the positioning member 200 defines the intersection angle θ1 between the flat surface of the backing plate 100 and the rotation shaft 6 to be vertical by preventing contact between the backing plate 100 and the cylindrical portion 21. By defining the intersection angle θ1 between the flat surface of the backing plate 100 and the rotation shaft 6 to be vertical, it is possible to more stabilize the contact between the opposing surface 71 of the bearing 7 and the rear surface 101 (flat surface) of the backing plate 100.

[0064] Furthermore, the positioning member 200 of the first embodiment determines the position of the backing plate 100 so that the rear surface 101 (flat portion) of the backing plate 100 and the opposing surface 71 of the bearing 7 are in surface contact. For example, the positioning member 200 prevents contact between the backing plate 100 and the cylindrical portion 21, thereby causing the flat portion of the backing plate 100 and the opposing surface 71 of the bearing 7 to be in surface contact. Here, "surface contact" as used in this disclosure refers to a state in which surfaces that are parallel to each other or can be considered parallel to each other are in surface contact. By determining the position of the backing plate 100 so that the rear surface 101 of the backing plate 100 and the opposing surface 71 of the bearing 7 are in surface contact, it is possible to suppress the generation of vibrations and noise during operation of the pump 1.

[0065] 5, in the pump 1 of the first embodiment, a gap Sp4 is formed between the positioning member 200 and the tubular portion 21. More specifically, the gap Sp4 is formed between the side peripheral portion 201 of the positioning member 200 and the side peripheral portion 212 of the tubular portion 21. In addition, the gap Sp4 is formed between the bottom portion 203 of the positioning member 200 and the bottom portion 211 of the tubular portion 21.

[0066] 5 shows a state in which the rotating shaft 6 is assembled at an angle relative to the cylindrical portion 21. Even when the rotating shaft 6 is assembled at an angle relative to the cylindrical portion 21, the presence of a gap Sp4 between the positioning member 200 and the cylindrical portion 21 causes the positioning member 200 to tilt relative to the cylindrical portion 21 in accordance with the tilt angle of the rotating shaft 6. As the positioning member 200 tilts relative to the cylindrical portion 21 in accordance with the tilt angle of the rotating shaft 6, the intersection angle θ2 between the rear surface 202 of the positioning member 200 and the rotating shaft 6 is maintained perpendicular.

[0067] By keeping the intersection angle θ2 between the rear surface 202 of the positioning member 200 and the rotation axis 6 vertical, the intersection angle θ1 between the flat surface (rear surface 101) of the receiving plate 100 and the rotation axis 6 can be kept vertical, making the contact between the opposing surface 71 of the bearing 7 and the rear surface 101 (flat surface) of the receiving plate 100 more stable.

[0068] (2.9) Elastic member The elastic member 300 is located in the extension direction D1 between the positioning member 200 and the tubular portion 21, which is a part of the pump case 2. More specifically, the elastic member 300 is located between the bottom 203 of the positioning member 200 and the bottom 211 of the tubular portion 21 in the extension direction D1.

[0069] The elastic member 300 in the first embodiment is cylindrical. The elastic member 300 is made of, for example, rubber, and functions as a displacement absorber for at least one of the tubular portion 21 of the pump case 2 and the positioning member 200. The provision of the elastic member 300 in the pump 1 can suppress the propagation of vibrations generated when the impeller 9 rotates to the tubular portion 21 of the pump case 2.

[0070] (2.10) Impeller 1, the impeller 9 of the first embodiment is integrally formed with the rotor portion 8. The impeller 9 is located in front of the rotor portion 8. The impeller 9 is located in the first space Sp1 of the pump chamber Sp3.

[0071] The impeller 9 has a front shroud 91 (first shroud) and a rear shroud 92 (second shroud). As shown in Fig. 1, the front shroud 91 and the rear shroud 92 are aligned in the extension direction D1. More specifically, a rear surface 910 of the front shroud 91 and a front surface 923 of the rear shroud 92 face each other in the extension direction D1.

[0072] The rear shroud 92 is formed in an annular shape having an inner edge 921 and an outer edge 922 .

[0073] The front shroud 91 is located forward of the rear shroud 92. The front shroud 91 is formed in an annular shape having an inner edge 94 and an outer edge 95.

[0074] As shown in Fig. 6, a plurality of blade portions 93 (13 blade portions in the example of Fig. 6) are formed on the front shroud 91, facing each other in the rotation direction (circumferential direction D3). In other words, the impeller 9 has a plurality of blade portions 93. In the following description, each of the plurality of blade portions 93 may be referred to as a "blade portion 93."

[0075] The blade portions 93 protrude rearward from the rear surface 910 of the front shroud 91 along the extension direction D1 (see FIG. 1). In other words, the blade portions 93 protrude toward the front surface 923 of the rear shroud 92 along the extension direction D1. A height H0 of the blade portions 93 in the extension direction D1 of the first embodiment is approximately equal to the distance along the extension direction D1 between the rear surface 910 of the front shroud 91 and the front surface 923 of the rear shroud 92.

[0076] In a plan view along extension direction D1, blade portion 93 is formed in an arc-shaped plate shape from inner edge portion 94 to outer edge portion 95. Blade portion 93 has a first surface 931 and a second surface 932. Impeller 9 of embodiment 1 rotates in a direction from second surface 932 to first surface 931 along circumferential direction D3 of front shroud 91.

[0077] A plurality of flow passages 96 (13 in the example of FIG. 6) are formed between the plurality of blade portions 93. In other words, the impeller 9 has a plurality of flow passages 96. In the following description, each of the plurality of flow passages 96 may be referred to as a "flow passage 96."

[0078] The flow path 96 is formed between two adjacent blade portions 93. More specifically, the flow path 96 is formed between a first surface 931 of one of the two adjacent blade portions 93 and a second surface 932 of the other of the two adjacent blade portions 93. In other words, the flow path 96 is formed between a certain first surface 931 and a second surface 932 opposing the certain first surface 931. The flow path 96 is also formed from an inner edge portion 94 to an outer edge portion 95 of the front shroud 91 (impeller 9). When the impeller 9 rotates, liquid flows in the flow path 96 from an inlet 961 located at the inner edge portion 94 toward an outlet 962 located at the outer edge portion 95.

[0079] Moreover, the flow path 96 of the first embodiment is formed by a plurality of blade portions 93 and a pair of members (a front shroud 91 and a rear shroud 92) that respectively cover both sides of the plurality of blade portions 93. More specifically, the flow path 96 is sandwiched between two adjacent blade portions 93 in the circumferential direction D3, and is sandwiched between a rear surface 910 of the front shroud 91 and a front surface 923 of the rear shroud 92 in the extension direction D1. The flow path 96 of the first embodiment is partitioned from the pump chamber Sp3 in the extension direction D1 and the circumferential direction D3.

[0080] FIG. 9 is a graph showing the relationship between the cross-sectional area of ​​the flow channel 96 and the position of the flow channel 96 between the inlet 961 and the outlet 962 in the first embodiment.

[0081] In the present disclosure, the "cross-sectional area of ​​the flow path 96" may include the area of ​​a cross section of the flow path 96 that intersects with the flow direction of the flowing liquid when the pump 1 is operating (when the impeller 9 is rotating). As shown in FIG. 8 , the cross-sectional area of ​​the flow path 96 in the first embodiment is the area of ​​a cross section in which the height H0 is the distance from the rear surface 910 of the front shroud 91 to the rear end of the blade portion 93 along the extension direction D1 (the height of the blade portion 93), and the width W0 is the length of a perpendicular line from the second surface 932 to the first surface 931 opposite the second surface 932. Note that the width W0 may also be the length of a perpendicular line from the first surface 931 to the second surface 932 opposite the first surface 931. Note that in the present disclosure, the cross-sectional area of ​​the flow path 96 is expressed with the cross-sectional area of ​​the inlet 961 being 100%.

[0082] 6, the cross sections of the inlet 961, the outlet 962, and the throttle portion 963 are illustrated by dotted regions. In the first embodiment, the width W1 of the cross section of the inlet 961 is the length of a perpendicular line from a portion of the first surface 931 closest to the inner edge 94 to a second surface 932 opposite the first surface 931. The height H1 of the cross section of the inlet 961 is the length along the extension direction D1 of a portion of the first surface 931 (blade portion 93) closest to the inner edge 94. In the first embodiment, the width W2 of the cross section of the outlet 962 is the length along the extension direction D1 of a portion of the second surface 932 opposite the first surface 931 closest to the outer edge 95. The height H2 of the cross section of the outlet 962 is the length along the extension direction D1 of a portion of the second surface 932 (blade portion 93) closest to the outer edge 95.

[0083] As shown in FIG. 7 , in the present disclosure, the "position of the flow path 96" is expressed as a ratio of a second distance L2 from the inlet 961 to a certain position to the first distance L1 (second distance L2 / first distance L1 [%]), where the first distance L1 from the inlet 961 to the outlet 962 is taken as 100%. The first distance L1 is defined, for example, as the length of the first surface 931 or the second surface 932 from the inlet 961 to the outlet 962 in a plan view along the extension direction D1. The first distance L1 in the first embodiment is the length of the first surface 931 from the inlet 961 to the outlet 962. The second distance L2 is defined, for example, as the length of the first surface 931 or the second surface 932 from the inlet 961 to the throttle portion 963 in a plan view along the extension direction D1. The second distance L2 in the first embodiment is the length of the first surface 931 from the inlet 961 to the throttle portion 963.

[0084] The flow path 96 has a throttle portion 963. The second distance L2 of the throttle portion 963 in the first embodiment is set to 19% of the first distance L1. As shown in FIG. 9 , the cross-sectional area of ​​the throttle portion 963, in which the second distance L2 is 19% of the first distance L1, is smaller than the cross-sectional area of ​​the inlet 961 and the cross-sectional area of ​​the outlet 962.

[0085] Because the cross-sectional area of ​​the throttle portion 963 is smaller than the cross-sectional area of ​​the inlet 961 and the cross-sectional area of ​​the outlet 962, the throttle portion 963 pressurizes the liquid passing through the throttle portion 963. Because the throttle portion 963 pressurizes the liquid, the pump 1 of embodiment 1 can suppress the occurrence of cavitation. When cavitation occurs in the flow path, the range through which the liquid flows narrows and the work efficiency of the pump decreases, but the pump 1 of embodiment 1 suppresses the decrease in work efficiency by suppressing the occurrence of cavitation. Furthermore, the pump 1 of embodiment 1 can suppress the occurrence of vibration and noise during operation of the pump 1 by suppressing the occurrence of cavitation.

[0086] 7, the second distance L2 (19%) between the inlet 961 and the throttle portion 963 in the first embodiment is shorter than the third distance L3 (81%) between the outlet 962 and the throttle portion 963. The third distance L3 is defined by, for example, the length of the first surface 931 or the second surface 932 from the outlet 962 to the throttle portion 963 in a plan view along the extension direction D1. The third distance L3 in the first embodiment is the length of the first surface 931 from the outlet 962 to the throttle portion 963. The second distance L2 being shorter than the third distance L3 can further suppress the occurrence of cavitation. In other words, the throttle portion 963 being located closer to the inlet 961 between the inlet 961 and the outlet 962 can further suppress the occurrence of cavitation.

[0087] Furthermore, the second distance L2 (19%) between the inlet 961 and the throttle portion 963 in the first embodiment is 10% or more of the first distance L1 between the inlet 961 and the outlet 962. By making the second distance L2 10% or more of the first distance L1, the occurrence of cavitation can be further suppressed. Note that the second distance L2 between the inlet 961 and the throttle portion 963 is preferably 10% to 30% of the first distance L1. Furthermore, the second distance L2 between the inlet 961 and the throttle portion 963 is more preferably 15% to 25% of the first distance L1. Furthermore, like the throttle portion 963 in the first embodiment, the second distance L2 between the inlet 961 and the throttle portion 963 is more preferably 18% to 22% of the first distance L1. Furthermore, the second distance L2 between the inlet 961 and the throttle portion 963 is more preferably 20% of the first distance L1. The throttle portion is not limited to a throttle portion formed over one cross section of the flow path 96, and may be formed to have a predetermined length in the longitudinal direction of the flow path 96.

[0088] 9, the cross-sectional area of ​​the flow path 96 in the first embodiment gradually decreases from the inlet 961 toward the throttle portion 963. Since the cross-sectional area of ​​the flow path 96 gradually decreases from the inlet 961 toward the throttle portion 963, the liquid can flow smoothly through the flow path 96.

[0089] 6 and 8, the height H0 of the plurality of blade portions 93 in the first embodiment gradually decreases from the inlet 961 toward the throttle portion 963. By gradually decreasing the height H0 of the plurality of blade portions 93 from the inlet 961 toward the throttle portion 963, the cross-sectional area of ​​the flow path 96 can be reduced without narrowing the width W0 of the flow path 96. Note that the cross-sectional area of ​​the flow path 96 may be reduced by changing the thickness of the blade portions 93 to gradually narrow the width W0 of the flow path 96 from the inlet 961 toward the throttle portion 963.

[0090] Furthermore, in the throttle portion 963 of the first embodiment, the height H3 of the throttle portion 963 is lower than the height H1 of the inlet 961. By making the height H3 of the throttle portion 963 lower than the height H1 of the inlet 961, the cross-sectional area of ​​the flow path 96 can be reduced without narrowing the width W0 (width W3) of the flow path 96.

[0091] As shown in FIG. 9 , in the first embodiment, in which the second distance L2 is 19% of the first distance L1, the cross-sectional area of ​​the throttle portion 963 is 85% or less of the cross-sectional area of ​​the inlet 961 or the outlet 962. By making the cross-sectional area of ​​the throttle portion 963 85% or less of the cross-sectional area of ​​the inlet 961 or the outlet 962, the occurrence of cavitation can be further suppressed. Furthermore, the cross-sectional area of ​​the throttle portion 963 is preferably 75% or less of the cross-sectional area of ​​the inlet 961 or the outlet 962. By making the cross-sectional area of ​​the throttle portion 963 75% or less of the cross-sectional area of ​​the inlet 961 or the outlet 962, the occurrence of cavitation can be further suppressed. Furthermore, the cross-sectional area of ​​the throttle portion 963 is more preferably 70% of the cross-sectional area of ​​the inlet 961 or the outlet 962.

[0092] 9, the cross-sectional area of ​​the throttle portion 963 in embodiment 1, in which the second distance L2 is 19% of the first distance L1, is 55% or more of the cross-sectional area of ​​the inlet 961 or the outlet 962. By maintaining the amount of liquid flowing through the flow path 96 at a constant level or more, the work efficiency of the pump 1 can be maintained at a constant level or more. Furthermore, the cross-sectional area of ​​the throttle portion 963 is preferably 65% ​​or more of the cross-sectional area of ​​the inlet 961 or the outlet 962. Furthermore, the cross-sectional area of ​​the throttle portion 963 is more preferably 70% of the cross-sectional area of ​​the inlet 961 or the outlet 962.

[0093] (3) Pump operation Next, the operation of the pump 1 will be described with reference to FIGS.

[0094] First, the control unit 43 of the drive unit 3 controls the energization of the multiple coils 42. Then, the rotor unit 8 rotates due to the interaction between the magnetic field generated by the current flowing through the multiple coils 42 and the magnetic field of the magnets 82 with multiple magnetic poles that the rotor unit 8 has. The rotation of the rotor unit 8 rotates the impeller 9 that is formed integrally with the rotor unit 8.

[0095] Centrifugal force is generated by the rotation of the impeller 9. The centrifugal force causes the liquid in the pump chamber Sp3 to be discharged from the discharge port 24 and then sucked into the pump chamber Sp3 through the suction port 22. In other words, the rotation of the impeller 9 causes the pump 1 to suck in and discharge the liquid.

[0096] Furthermore, when the impeller 9 rotates, a thrust acts on the impeller 9 in a direction (forward) along the extension direction D1 toward the suction section 22. The thrust causes the impeller 9, rotor section 8, bearing 7, and backing plate 100 to move forward as a unit. As shown in FIG. 2, the front surface 102 of the backing plate 100 comes into contact with the rear surface 202 of the positioning member 200, thereby determining the positions of the impeller 9, rotor section 8, bearing 7, and backing plate 100 in the extension direction D1. The bearing 7 rotates with the opposing surface 71 of the bearing 7 in contact with the rear surface 101 of the backing plate 100.

[0097] When the control unit 43 of the drive unit 3 performs control to stop the supply of power to the plurality of coils 42, the rotation of the rotor unit 8 stops, and the operation of the pump 1 stops.

[0098] (4) Variations The first embodiment is merely one of various embodiments of the present disclosure, and various modifications can be made to the first embodiment depending on the design and the like, as long as the object of the present disclosure can be achieved.

[0099] Below, we will list some modified examples of embodiment 1. The modified examples described below can be applied in appropriate combination with embodiment 1.

[0100] (4.1) First Modification As shown in FIG. 10, the pump 1 may include a positioning member 200a instead of the positioning member 200.

[0101] The positioning member 200a has a plurality of retaining portions 207 (two in the example of FIG. 10).

[0102] The plurality of retaining portions 207 protrude from the plane 205 in a direction perpendicular to the extension direction D1. The positioning member 200a has the plurality of retaining portions 207, which can prevent the rotation shaft 6 from coming off the positioning member 200a.

[0103] (4.2) Second Modification 11, the pump 1 may include a positioning member 200b instead of the positioning member 200, and an elastic member 300a instead of the elastic member 300. In the embodiment shown in FIG.

[0104] As shown in FIG. 12, the positioning member 200 b has a protrusion 208 .

[0105] The protruding portion 208 protrudes (forward) from the bottom portion 203 along the extension direction D1 toward the tubular portion 21 of the pump case 2. The shape of the protruding portion 208 is cylindrical with a rounded front surface. In addition, since the protruding portion 208 is formed on the bottom portion 203, an annular groove is formed between the protruding portion 208 and the edge portion 204.

[0106] 13, the side periphery 201 of the positioning member 200b is thicker than the side periphery 201 (see FIG. 4) of the positioning member 200. The side periphery 201 of the positioning member 200b has a cylindrical shape.

[0107] The positioning member 200b has a plurality of grooves 209 (two in the example of FIG. 13). The plurality of grooves 209 are formed on the inner circumferential surface of the side circumferential portion 201 along the extension direction D1. More specifically, the plurality of grooves 209 are formed on both ends of the flat surface 205. Since the positioning member 200b has a plurality of grooves 209, when the rotating shaft 6 is inserted, the inner circumferential surface of the side circumferential portion 201 elastically bends, making it possible to prevent the rotating shaft 6 from coming out.

[0108] 11 , elastic member 300a has an annular shape. Elastic member 300a is arranged to fit into an annular groove formed between protruding portion 208 and edge portion 204 of positioning member 200b. Elastic member 300a protrudes forward from protruding portion 208 while positioned in the annular groove formed between protruding portion 208 and edge portion 204 of positioning member 200b. Providing elastic member 300a in pump 1 can suppress vibrations generated during rotation of impeller 9 from being transmitted to tubular portion 21 of pump case 2.

[0109] (4.3) Third Modification As shown in FIG. 14, the pump 1 may include a positioning member 200c instead of the positioning member 200b.

[0110] The positioning member 200c does not have the edge 204 that the positioning member 200b according to the second modification has. In addition, the bottom 203 of the positioning member 200 is formed so as to protrude rearward near the outer edge as it approaches the outer edge.

[0111] 15, in the pump 1 according to the third modification, an elastic member 300a is fitted around the protruding portion 208 of the positioning member 200c. By fitting the elastic member 300a around the protruding portion 208, the elastic member 300a comes into contact with the tubular portion 21 of the pump case 2 in the extension direction D1 and the radial direction D2 within the tubular portion 21, and it is possible to suppress the propagation of vibrations generated when the impeller 9 rotates to the tubular portion 21 of the pump case 2.

[0112] (4.4) Other Modifications The plurality of blade portions 93 may be formed on the rear shroud 92 instead of the front shroud 91. Also, the plurality of blade portions 93 may be formed in a distributed manner on the front shroud 91 and the rear shroud 92.

[0113] Instead of the molded part 4, the driving part 3 may have a mechanism for rotating a plurality of driving magnets around the separation plate 5 along the circumferential direction D3.

[0114] In the first embodiment, the case where the drive unit 3 has the separation plate 5 has been exemplified, but the pump case 2 may have the separation plate 5 instead of the drive unit 3. Also, instead of the drive unit 3 having the separation plate 5, at least one of the pump case 2 and the molded unit 4 may have a shape that functions as the separation plate 5. For example, the inner periphery of the molded unit 4 may be resin-molded to prevent water from entering the inside of the molded unit 4 from the pump chamber Sp3.

[0115] (Embodiment 2) As shown in FIG. 16, the pump 1 according to the second embodiment differs from the pump 1 according to the first embodiment in that it includes a positioning member 200d instead of the positioning member 200 and an elastic member 300b instead of the elastic member 300.

[0116] The rotating shaft 6 of the second embodiment has a groove 63. The groove 63 is formed over the entire circumference of the first end 61 in the circumferential direction.

[0117] The positioning member 200d is located in the extension direction D1 between the receiving plate 100 and the tubular portion 21, which is a part of the pump case 2. A gap Sp4 is formed between the positioning member 200d and the rear end of the side peripheral portion 212 of the tubular portion 21. Due to the presence of the gap Sp4, even if the rotating shaft 6 is assembled at an angle with respect to the tubular portion 21, the positioning member 200d will be inclined with respect to the tubular portion 21 in accordance with the angle of inclination of the rotating shaft 6.

[0118] The positioning member 200d is a flat plate-like member. The positioning member 200d of the second embodiment is an annular flat plate having a through hole 210 through which the first end 61 of the rotating shaft 6 passes. The through hole 210 is semicircular in shape. The through hole 210 is configured so that when the first end 61 of the rotating shaft 6 is passed through the through hole 210, the positioning member 200d does not rotate with respect to the rotating shaft 6 (first end 61).

[0119] Furthermore, the through-hole 210 of the second embodiment is formed to fit into the groove 63 of the rotating shaft 6. That is, the positioning member 200d is formed to fit into the groove 63 of the rotating shaft 6. The positioning member 200d is fixed to the rotating shaft 6, and the positioning member 200d does not move along the extension direction D1. Therefore, a gap Sp4 between the positioning member 200d and the rear end of the side peripheral portion 212 of the tubular portion 21 is maintained.

[0120] The pump 1 of the second embodiment includes the flat plate-shaped positioning member 200d, and therefore, the manufacturing cost can be reduced compared to when, for example, a bottomed cylindrical positioning member 200 is included.

[0121] Elastic member 300b is located between first end 61 of rotating shaft 6 and tubular portion 21, which is a part of pump case 2. Providing elastic member 300b in pump 1 makes it possible to suppress the propagation of vibrations generated when impeller 9 rotates to tubular portion 21, which is a part of pump case 2.

[0122] The second embodiment is merely one of various embodiments of the present disclosure, and various modifications can be made to the second embodiment depending on the design and the like, as long as the object of the present disclosure can be achieved.

[0123] For example, the positioning member 200d may be a member configured to be fixed to the rotating shaft 6 by an elastic force acting along the radial direction D2 toward the axis Ax1 of the rotating shaft 6 when the rotating shaft 6 is inserted through the through hole 210. The positioning member 200d may be a so-called e-ring or the like. That is, the positioning member 200d may be a member having a C-shape in a planar view. More specifically, the positioning member 200d may be a flat plate-like member having a C-shape in a planar view. In the present disclosure, the term "C-shape in a planar view" may include a shape in which a portion of a ring having a through hole (through hole 210) is missing. Furthermore, the through hole 210 (space) through which the rotating shaft 6 passes includes a space that completely surrounds the periphery of the rotating shaft 6 and a space in which a portion of the periphery of the rotating shaft 6 is missing.

[0124] The various configurations (including modified examples) described in the second embodiment can be adopted in appropriate combination with the various configurations (including modified examples) described in the first embodiment.

[0125] (summary) As described above, the pump (1) according to the first aspect includes the pump case (2), the rotating shaft (6), the bearing (7), the impeller (9), the drive unit (3), the backing plate (100), and the positioning members (200; 200a; 200b; 200c; 200d). The pump case (2) forms at least a portion (first space Sp1) of the pump chamber (Sp3). The rotating shaft (6) is located inside the pump chamber (Sp3), and one end (first end 61) is inserted into a portion (cylindrical portion 21) of the pump case (2). The rotating shaft (6) passes through the bearing (7). The impeller (9) has a fluid flow path (96). The drive unit (3) rotates the impeller (9) about the rotating shaft (6) as a rotation center to cause the fluid to flow. The rotating shaft (6) passes through the backing plate (100). The backing plate (100) is located between the bearing (7) and a part of the pump case (2) in the extension direction (D1) of the rotating shaft (6) and is in contact with the opposing surface (71) of the bearing (7). The positioning members (200; 200a; 200b; 200c; 200d) are located between the backing plate (100) and a part (tubular portion 21) of the pump case (2) in the extension direction (D1) and determine the position of the backing plate (100) in the extension direction (D1).

[0126] According to this aspect, the positioning members (200; 200a; 200b; 200c; 200d) determine the position of the backing plate (100) in the extension direction (D1), thereby preventing the backing plate (100) from contacting a portion of the pump case (2) (the cylindrical portion 21). For example, even if the rotating shaft (6) is attached at an angle with respect to a portion of the pump case (2), preventing the backing plate (100) from contacting a portion of the pump case (2) can prevent the backing plate (100) from tilting with respect to the rotating shaft (6). Preventing the backing plate (100) from tilting with respect to the rotating shaft (6) stabilizes contact between the opposing surface (71) of the bearing (7) and the rear surface of the backing plate (100), thereby reducing noise and vibration during operation of the pump (1).

[0127] In the pump (1) according to the second aspect, in the first aspect, the positioning members (200; 200a; 200b; 200c; 200d) define the intersection angle (θ1) between the flat surface (rear surface 101) of the backing plate (100) and the rotation axis (6).

[0128] According to this embodiment, the positioning members (200; 200a; 200b; 200c; 200d) determine the intersection angle (θ1) between the flat surface (rear surface 101) of the receiving plate (100) and the rotation axis (6), thereby further preventing the receiving plate (100) from tilting relative to the rotation axis (6).

[0129] In the pump (1) according to the third embodiment, in the second embodiment, the intersection angle (θ1) between the flat surface (rear surface 101) of the backing plate (100) and the rotation shaft (6) is perpendicular.

[0130] According to this embodiment, by defining the intersection angle (θ1) between the flat surface (rear surface 101) of the receiving plate (100) and the rotation axis (6) as perpendicular, the contact between the opposing surface (71) of the bearing (7) and the flat surface of the receiving plate (100) can be made more stable.

[0131] In the pump (1) according to the fourth aspect, in any of the first to third aspects, the positioning member (200; 200a; 200b; 200c; 200d) determines the position of the backing plate (100) so that the flat portion (rear surface 101) of the backing plate (100) and the opposing surface (71) of the bearing (7) are in surface contact.

[0132] According to this embodiment, by determining the position of the receiving plate (100) so that the flat surface (rear surface 101) of the receiving plate (100) and the opposing surface (71) of the bearing (7) are in surface contact, it is possible to suppress the generation of noise and vibration during operation of the pump (1).

[0133] In the pump (1) according to the fifth aspect, in any one of the first to fourth aspects, a part (the cylindrical portion 21) of the pump case (2) is the cylindrical portion (21) formed in a bottomed cylindrical shape so that one end (the first end portion 61) of the rotary shaft (6) can be inserted therein. A gap (Sp4) is formed between the positioning member (200; 200a; 200b; 200c; 200d) and the cylindrical portion (21).

[0134] According to this aspect, even if the rotating shaft (6) is assembled at an angle relative to the cylindrical portion (21), the presence of a gap (Sp4) between the positioning members (200; 200a; 200b; 200c; 200d) and the cylindrical portion (21) causes the positioning members (200; 200a; 200b; 200c; 200d) to tilt relative to the cylindrical portion (21) in accordance with the tilt angle of the rotating shaft (6). The positioning members (200; 200a; 200b; 200c; 200d) tilt relative to the cylindrical portion (21) in accordance with the tilt angle of the rotating shaft (6), thereby maintaining the intersection angle (θ2) between the flat surface (rear surface 202) of the positioning member (200; 200a; 200b; 200c; 200d) and the rotating shaft (6). By maintaining the intersection angle (θ2) between the flat surface of the positioning member (200; 200a; 200b; 200c; 200d) and the rotation axis (6), the intersection angle (θ1) between the flat surface (rear surface 101) of the receiving plate (100) and the rotation axis (6) can be maintained, and the contact between the opposing surface (71) of the bearing (7) and the flat surface of the receiving plate (100) can be made more stable.

[0135] In the pump (1) according to a sixth aspect, in any one of the first to fifth aspects, the positioning member (200; 200a; 200b; 200c) is formed in a cylindrical shape with a bottom so as to cover one end (first end 61) of the rotating shaft (6). The one end of the rotating shaft (6) is inserted into a part (cylindrical portion 21) of the pump case (2) via the positioning member (200; 200a; 200b; 200c).

[0136] According to this embodiment, by making the positioning member (200; 200a; 200b; 200c) cover one end (first end 61) of the rotating shaft (6), the positioning member (200; 200a; 200b; 200c) can be more firmly fixed to the rotating shaft (6).

[0137] The pump (1) according to a seventh aspect is the pump (1) of the sixth aspect, further including an elastic member (300; 300a). The elastic member (300; 300a) is located between the positioning member (200; 200a; 200b; 200c) and a part (tubular portion 21) of the pump case (2) in the extension direction (D1).

[0138] According to this aspect, the pump (1) is provided with the elastic member (300; 300a), which can prevent vibrations generated when the impeller (9) rotates from being transmitted to a part (tubular portion 21) of the pump case (2).

[0139] In the pump (1) according to the eighth aspect, in any one of the first to fifth aspects, the positioning member (200d) is a flat plate-like member having a through-hole (210) through which the rotating shaft (6) passes, and is fixed to the rotating shaft (6).

[0140] According to this aspect, the cost of the positioning member (200d) can be reduced compared to when the positioning member is, for example, a cylindrical member with a bottom.

[0141] The pump (1) according to a ninth aspect is the pump (1) of the eighth aspect, further including an elastic member (300b). The elastic member (300b) is located between one end (first end 61) of the rotary shaft (6) and a part (tubular portion 21) of the pump case (2) in the extension direction (D1).

[0142] According to this aspect, the pump (1) includes the elastic member (300b), which can prevent vibrations generated during rotation of the impeller (9) from being transmitted to a part (the cylindrical portion 21) of the pump case (2).

[0143] The configurations other than those of the first embodiment are not essential for the pump (1) and can be omitted as appropriate. [Explanation of symbols]

[0144] 1 pump 2 Pump case 21 Cylinder part 3 Drive unit 6 Rotation Axis 61 First end (one end) 7. Bearings 71 Opposite surface 9 Impeller 96 Flow path 100 catch plate 101 Rear surface (flat surface) 200, 200a, 200b, 200c, 200d Positioning members 210 Through hole 300, 300a, 300b Elastic member D1 Stretching direction Sp3 Pump Room Sp4 Gap θ1 Intersection angle

Claims

1. a pump case that defines at least a portion of a pump chamber; a rotating shaft located inside the pump chamber, one end of which is inserted into a part of the pump case; a bearing through which the rotating shaft passes; an impeller having a fluid flow path; a drive unit that rotates the impeller around the rotation shaft as a rotation center to cause the fluid to flow; a receiving plate through which the rotary shaft passes, the receiving plate being positioned between the bearing and the portion of the pump case in the extending direction of the rotary shaft and being in contact with an opposing surface of the bearing; a positioning member positioned between the backing plate and the portion of the pump case in the extension direction and defining a position of the backing plate in the extension direction; Equipped with the part of the pump case is a cylindrical portion formed into a bottomed cylindrical shape so that the one end of the rotary shaft can be inserted therein, A gap is formed between the positioning member and the cylindrical portion, The positioning member is tiltable with respect to the cylindrical portion. pump.

2. The positioning member defines an intersection angle between a flat surface of the receiving plate and the rotation axis.

2. The pump of claim 1.

3. The intersection angle between the planar portion of the receiving plate and the rotation axis is perpendicular.

3. The pump of claim 2.

4. the positioning member determines the position of the backing plate so that a flat portion of the backing plate and the opposing surface of the bearing are in surface contact with each other. A pump according to any one of claims 1 to 3.

5. The positioning member is formed in a cylindrical shape with a bottom so as to cover the one end of the rotating shaft, the one end of the rotating shaft is inserted into the part of the pump case via the positioning member; A pump according to any one of claims 1 to 4.

6. Further comprising an elastic member positioned between the positioning member and the portion of the pump case in the extension direction.

6. The pump of claim 5.

7. The positioning member is a flat plate-like member having a through hole through which the rotation shaft passes and is fixed to the rotation shaft. A pump according to any one of claims 1 to 4.

8. The pump further comprises an elastic member positioned between the one end of the rotating shaft and the part of the pump case in the extension direction.

8. The pump of claim 7.

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