CN117460892A - Bearing structure of shielding electric pump - Google Patents
Bearing structure of shielding electric pump Download PDFInfo
- Publication number
- CN117460892A CN117460892A CN202280039152.5A CN202280039152A CN117460892A CN 117460892 A CN117460892 A CN 117460892A CN 202280039152 A CN202280039152 A CN 202280039152A CN 117460892 A CN117460892 A CN 117460892A
- Authority
- CN
- China
- Prior art keywords
- bearing
- housing
- supported member
- axial direction
- rotor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000007788 liquid Substances 0.000 claims abstract description 40
- 239000000463 material Substances 0.000 claims abstract description 19
- 238000010276 construction Methods 0.000 claims description 5
- 230000002093 peripheral effect Effects 0.000 description 12
- 230000004308 accommodation Effects 0.000 description 4
- 239000000314 lubricant Substances 0.000 description 4
- 239000002184 metal Substances 0.000 description 4
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 description 3
- 229910010271 silicon carbide Inorganic materials 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A bearing structure of a canned motor pump is provided with: a rotation shaft (2) that rotates integrally with a rotor (12) of the motor unit (11); bearings (3 a, 3 b) which are fitted into casing-side bearing housings (32 a, 32 b) provided in a pump section (31) via an elastic sheet material (33) and rotatably support a rotary shaft (2) in the vertical direction; a supported member (4 a, 4 b) which is fixed to the rotary shaft (2) in the axial direction between the rotor (12) of the motor unit (11) and the bearings (3 a, 3 b) and is rotatably supported by the bearings (3 a, 3 b) in the axial direction; and impellers (6 a, 6 b) that rotate integrally with the rotary shaft (2), wherein an elastic reaction force is imparted in the axial direction when the bearings (3 a, 3 b) are pressed by the bearing support members (4 a, 4 b) to the side opposite to the rotor (12) in a canned electric pump (8) in which a part of the liquid that is transported by the rotation of the impellers (6 a, 6 b) flows between the rotary shaft (2) and the bearings (3 a, 3 b).
Description
Technical Field
The present invention relates to a bearing structure of a canned motor pump.
The present application claims priority based on japanese patent application No. 2021-094287, filed on 4/6/2021, the contents of which are incorporated herein by reference.
Background
Conventionally, a canned motor pump is known in which a part of the liquid supplied from a pump is caused to flow between a rotary shaft and a bearing and used as a lubricant (see, for example, patent document 1).
The canned motor pump disclosed in patent document 1 includes: a slide bearing (hereinafter referred to as "radial bearing") that supports the rotary shaft in a direction perpendicular to the axial direction, and a slide bearing (hereinafter referred to as "axial bearing") that is fixed to the rotary shaft. The axial bearing restricts movement of the rotating shaft in the axial direction by bringing its abutment surface into contact with a side surface of the radial bearing in the axial direction.
A constant gap for allowing a part of the liquid supplied from the pump to flow is provided between the rotary shaft and the radial bearing. Although not described in patent document 1, in many cases, the radial bearing is fitted into the bearing housing through an elastic thin plate material such as a tolerance ring.
Prior art literature
Patent literature
Patent document 1: japanese patent No. 3897931
Disclosure of Invention
Problems to be solved by the invention
In the bearing structure of the canned motor pump, there is a case where the side surfaces of the radial bearing and the contact surfaces of the axial bearing are not in surface contact when they are inclined relatively to each other due to the influence of dimensional tolerances of the respective parts. In this case, the wear of the side surface portions of the radial bearing and the contact surface portions of the axial bearing progresses, and the initial axial play of the rotary shaft and the inclination of the rotary shaft with respect to the initial axial direction gradually increase, so that the performance of the pump may be reduced.
The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a bearing structure of a canned motor pump configured as follows: in a canned motor pump in which a part of the liquid supply is used as a lubricant between a rotary shaft and a bearing (radial bearing) that supports the rotary shaft in a direction perpendicular to the axial direction, the side surfaces of the bearing (radial bearing) and the abutment surface of a supported member (axial bearing) that is fixed to the rotary shaft in the axial direction are likely to be in surface contact with each other.
Solution for solving the problem
The precondition for the bearing structure of the canned motor pump according to claim 1 of the present invention is that the bearing structure of the canned motor pump comprises: a rotation shaft that rotates integrally with a rotor of the motor unit; a bearing which is fitted into a casing-side bearing housing provided in the pump section via an elastic thin plate material and rotatably supports the rotary shaft in a direction perpendicular to the axial direction; a supported member mounted on the rotary shaft between the bearing and the rotor of the motor unit, and rotatably supported by the bearing in an axial direction; and an impeller that rotates integrally with the rotation shaft, a part of the liquid that is transported by the rotation of the impeller flowing between the rotation shaft and the bearing, wherein the bearing structure of the canned motor pump is provided with the following elastic structure: when the bearing is pressed by the supported member to the side opposite to the rotor of the motor, an elastic reaction force is applied to one or both of the bearing and the supported member in the axial direction.
The bearing structure of a canned motor pump according to claim 2 of the present invention is the bearing structure of a canned motor pump according to claim 1, wherein the elastic structure is an elastic body provided between a side of the bearing opposite to the rotor of the motor unit and the housing-side bearing housing to apply the elastic reaction force to the bearing in an axial direction.
The bearing structure of a canned motor pump according to claim 3 of the present invention is the bearing structure of a canned motor pump according to claim 1, wherein the supported member is attached to the rotary shaft via a housing for the supported member. The elastic structure is an elastic body provided between the housing for the supported member and a side of the supported member, which is closer to the rotor of the motor unit, and imparts the elastic reaction force to the supported member in the axial direction.
The bearing structure of a canned motor pump according to claim 4 of the present invention is the bearing structure of a canned motor pump according to claim 1, wherein in the elastic structure, a plate material is provided between the housing-side bearing housing and a side of the bearing opposite to the rotor of the motor portion. Only a part of the surface of the plate material on the opposite side of the bearing is supported in the axial direction by the housing-side bearing housing, so that the elastic reaction force is imparted to the bearing in the axial direction.
The bearing structure of a canned motor pump according to claim 5 of the present invention is the bearing structure of a canned motor pump according to claim 1, wherein the supported member is fixed to the rotary shaft in the axial direction by means of a housing for the supported member. In the elastic structure, a plate material is provided between the side of the supported member against the rotor of the motor unit and the supported member housing, and only a part of a surface of the plate material on the opposite side to the supported member is supported in the axial direction by the supported member housing, so that the elastic reaction force is applied to the supported member in the axial direction.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, the bearing and the supported member are easily brought into surface contact with each other.
Drawings
Fig. 1 is a partial cross-sectional view of a canned motor pump according to the present embodiment.
Fig. 2 is an enlarged cross-sectional view of the periphery of the 1 st bearing of the present embodiment.
Fig. 3 is an enlarged view of a portion a in fig. 1.
Fig. 4 is an enlarged view of a portion B of fig. 1.
Fig. 5 is an enlarged cross-sectional view of the periphery of a connecting tube according to another embodiment.
Fig. 6 is an enlarged cross-sectional view of the periphery of another embodiment of the resilient construction.
Fig. 7 is an enlarged cross-sectional view of the periphery of the elastic structure of the present embodiment.
Fig. 8 is an enlarged cross-sectional view of the periphery of another embodiment of the resilient construction.
Fig. 9 is an enlarged cross-sectional view of the periphery of the elastic structure of the present embodiment.
Detailed Description
Hereinafter, a bearing structure of a canned motor pump according to an embodiment of the present invention will be described with reference to the drawings. As shown in fig. 1 to 4, the bearing structure 1 of the canned motor pump is composed of a rotary shaft 2, a bearing 3a, a bearing 3b, a supported member 4a, a supported member 4b, an impeller 6a, an impeller 6b, an elastic structure 7, and the like, which are included in a canned motor pump 8.
As shown in fig. 1, the canned motor pump 8 includes a motor unit 11 and a pump unit 31 driven by the motor unit 11. The motor unit 11 is a canned motor including a rotor 12 having magnets 27 and a stator 13 on the outer periphery of the rotor 12, and the rotary shaft 2 to which the rotor 12 is fixed is supported by bearings 3a and 3b mounted on a housing-side bearing housing 32a and a housing-side bearing housing 32b via a sleeve 25. The pump unit 31 includes: an impeller 6a, 6b fixed to the rotary shaft 2; and pump housings 16a and 16b each having an impeller housing space 14a and 14b for housing the impellers 6a and 6 b. The rotor 12 of the motor 11 is housed inside the stator shield 9. The stator 13 of the motor unit 11 is housed between the outer peripheral surface 17 of the stator shield 9 and the inner peripheral surface 19 of the cylindrical motor frame 18 at a position corresponding to the rotor 12 in the stator shield 9. The motor frame 18 houses the stator shield 9. The stator shield 9 is hermetically connected to the stator side plates 10 provided at both ends of the motor frame 18 by welding. The motor frame 18 and the stator side plates 10 provided at both ends of the motor frame 18 are sealed by the O-rings 5, and are hermetically connected by partial welding. The stator side plate 10, the housing side bearing housing 32a, and the housing side bearing housing 32b seal the internal space 66 with O-rings 15 disposed at both ends of the stator side plate 10. The pump casing 16a, the pump casing 16b, and the casing-side bearing housing 32a, 32b seal the impeller housing space 14a, 14b with the O-rings 20 disposed at both ends of the casing-side bearing housing 32a, 32b. Further, since a minute gap is formed between the inner peripheral surfaces of the bearings 3a and 3b and the sleeve 25, the bearings 3a and 3b can be inclined at a minute angle with respect to the axis. Hereinafter, the pump casing 16a will be referred to as "1 st pump casing 16a", and the pump casing 16b will be referred to as "2 nd pump casing 16b".
In addition, a portion of the outer peripheral surface 17 of the stator shield 9, where the stator core 21 is not present, is covered with the support tube 22. The support cylinder 22 has a cylindrical shape along the outer peripheral surface 17 of the stator shield 9.
The motor unit 11 includes a rotor 12 and a stator 13. The rotor 12 includes a rotor shield 23, a rotor side plate 24, a rotor body 26, magnets 27, a yoke 28, and the like. The rotor 12 is fixed to the rotary shaft 2 so as to rotate integrally with the rotary shaft 2. The rotary shaft 2 is supported by bearings 3a and 3b mounted on the housing-side bearing housing 32a and 32b via the sleeve 25. The rotor 12 includes a rotor body 26 fixed to the rotary shaft 2, and a yoke 28, a magnet 27, a rotor side plate 24, and a rotor shield 23 supported by the rotor body 26. The rotor shield 23 is joined to the rotor body 26 and the rotor side plates 24 by welding to seal the magnets 27 and the yokes 28. The rotor 12 is housed inside the stator shield 9 in the canned motor pump 8.
The stator 13 is constituted by an electromagnetic coil 29 or the like, and when a driving current is supplied to the stator 13, the rotor 12 and the rotary shaft 2 are driven to rotate.
The rotor 12 of the motor 11 is fixed to the rotary shaft 2, and rotates integrally with the rotor 12 of the motor 11.
As shown in fig. 1 to 4, the bearings 3a and 3b are fitted into a housing-side bearing housing 32a and a housing-side bearing housing 32b provided in the pump section 31 via an elastic thin plate member 33. The bearings 3a and 3b rotatably support the rotary shaft 2 in a direction perpendicular to the axial direction. The bearings 3a and 3b are cylindrical. Grooves 76 extending in the radial direction are formed in the axial end surfaces 34 of the bearings 3a and 3b, and spiral grooves 74 are formed in the inner peripheral wall 36. Any of the grooves 74, 76 is provided for flowing the liquid. As a material of the bearings 3a and 3b, siC (silicon carbide) excellent in heat resistance and durability is used, for example.
In the present embodiment, the bearings 3a and 3b are disposed on the outer periphery of the sleeve 25 as a member of the rotary shaft 2. As the material of the sleeve 25, a material excellent in heat resistance and durability is used similarly to the bearings 3a and 3b.
The bearings 3a and 3b are provided on both sides of the rotor 12 of the motor 11 in the axial direction of the rotary shaft 2. Hereinafter, the bearing 3a is referred to as "1 st bearing 3a", and the bearing 3b is referred to as "2 nd bearing 3b".
The bearings 3a and 3b are fitted into the housing-side bearing housing 32a and the housing-side bearing housing 32b. The housing-side bearing housing 32a and the housing-side bearing housing 32b are provided in the pump section 31.
The housing-side bearing housing 32a and the housing-side bearing housing 32b are provided on both sides of the rotor 12 of the motor portion 11 in the axial direction of the rotary shaft 2. Hereinafter, the two housing-side housings 32 are referred to as "1 st housing-side bearing housing 32a" and "2 nd housing-side bearing housing 32b", respectively.
As the elastic thin plate 33, in the present embodiment, a tolerance ring is used. The bearings 3a and 3b are fitted into the housing-side bearing housing 32a and the housing-side bearing housing 32b via the elastic thin plate member 33, and therefore, the bearings 3a and 3b are prevented from rattling with respect to the housing-side bearing housing 32a and the housing-side bearing housing 32b, and differences in thermal expansion coefficients between the housing-side bearing housing 32a and the housing-side bearing housing 32b and the bearings 3a and 3b are absorbed.
The rotary shaft 2 and the rotor 12 are provided with a bearing-supported member housing 38a and a bearing-supported member housing 38b that house the bearing-supported member 4a and the bearing-supported member 4b. The supported members 4a and 4b are fitted into the supported member case 38a and the supported member case 38b through the supported member elastic sheet 35. In the present embodiment, the elastic thin plate material 35 for the supported member also uses a tolerance ring. The bearing-supported housing 38a and the bearing-supported housing 38b are fixed to the rotary shaft 2 in the axial direction. The supported members 4a and 4b are attached to the rotary shaft 2 via the supported member housing 38a and the supported member housing 38b. Therefore, the rotary shaft 2 is supported by the bearings 3a and 3b in the axial direction by the supported members 4a, 4b, and the supported member housings 38a and 38b. A gap of a predetermined size is formed between the inner peripheral surfaces of the supported members 4a and 4b and the supported member housings 38a and 38b, and the supported members 4a and 4b can be inclined at a slight angle with respect to the axis.
The supported members 4a and 4b are also provided on both sides of the rotor 12 of the motor 11 in the axial direction of the rotary shaft 2. Specifically, the supported members 4a and 4b are attached to the rotary shaft 2 between the rotor 12 of the motor 11 and the bearings 3a and 3b, and are rotatably supported by the bearings 3a and 3b in the axial direction. SiC excellent in heat resistance and durability, for example, is used as the material of the supported member 4a and the supported member 4b.
Hereinafter, the supported member 4a supported by the 1 st bearing 3a is referred to as a "1 st supported member 4a", and the supported member 4b supported by the 2 nd bearing 3b is referred to as a "2 nd supported member 4b".
The impellers 6a and 6b rotate integrally with the rotary shaft 2. As shown in fig. 2 and 4, the impellers 6a and 6b include: a cylindrical impeller hub portion 39a and impeller hub portion 39b fixed to the rotary shaft 2; and annular plate-shaped impeller wing portions 45a and 45b connected to the impeller hub portions 39a and 39 b. The impeller hub portion 39a and the impeller hub portion 39b have: a rotation shaft fixing portion 47 having a cylindrical shape for fixing the impeller boss portion 39a and the impeller boss portion 39b to the rotation shaft 2; and an impeller wing connection portion 48 extending from the outer peripheral surface of the rotation shaft fixing portion 47 in the radial direction of the rotation shaft fixing portion 47, having a circular annular plate shape, and connected to the impeller wing 45a and the impeller wing 45 b. The impeller hub portions 39a and 39b are connected to the rotation center side end portions 46 of the impeller wing portions 45a and 45b at impeller wing connection portions 48. The impeller hub portion 39a and the impeller blade connecting portion 48 of the impeller hub portion 39b are provided with an impeller hub portion through hole 49a and an impeller hub portion through hole 49b that penetrate in the axial direction. The liquid flowing back from the stator shield 9 side passes through the impeller hub through hole 49a and the impeller hub through hole 49b. Further, the impeller hub portion 39a and the impeller blade connection portion 48 of the impeller hub portion 39b are provided with annular impeller hub portion protruding pieces 51a and impeller hub portion protruding pieces 51b extending toward the stator shield 9 to prevent backflow of the liquid. The impeller boss protruding pieces 51a and 51b are inserted into annular concave portions 53a and 53b formed in the inner wall surfaces 52 of the pump casing 16a and 16 b.
In the canned motor pump 8 of the present embodiment, the impeller 6a and the impeller 6b are provided at both axial ends of the stator can 9. Hereinafter, the impeller 6a is referred to as "1 st impeller 6a", and the impeller 6b is referred to as "2 nd impeller 6b".
A 1 st inlet port 56 is provided in a side surface of the 1 st pump casing 16a in which the 1 st impeller 6a is housed. A liquid supply port 57 for supplying the liquid having flowed into the 1 st pump casing 16a to the 2 nd pump casing 16b is provided on the upper surface of the 1 st pump casing 16 a.
The 1 st casing-side bearing housing 32a has a 1 st communication path 67 that communicates the 1 st impeller accommodation space 14a and the inner space 66 of the stator shield 9. The 1 st communication path opening 64 of the 1 st communication path 67 is located on the wall surface 63 of the 1 st impeller housing space 14a on the stator shield case 9 side, and is provided in the vicinity of the 1 st impeller hub portion through hole 49a at a position closer to the rotating shaft 2 than the 1 st impeller hub portion protruding piece 51 a.
The 1 st casing-side bearing housing 32a forms the 1 st impeller accommodation space 14a together with the 1 st pump casing 16 a. The 1 st casing-side bearing housing 32a has a 1 st recess 53a on a wall surface 63 on the stator shield 9 side that forms the 1 st impeller housing space 14a. The 1 st impeller hub portion protrusion piece 51a provided in the 1 st impeller hub portion 39a is inserted into the 1 st recess 53a.
Further, the 1 st turbine blade 45a is provided with a 1 st cylindrical seal plate 78 coaxially centered with the rotation shaft 2. The 1 st seal plate 78 extends in the axial direction of the rotary shaft 2 in the direction of the 1 st inlet port 56, and reduces the gap between the outer peripheral surface thereof and the inner wall 77 of the 1 st inlet port 56 in the 1 st pump casing 16 a. The 1 st seal plate 78 seals between the space in the 1 st inflow port 56 and the space formed by the outer wall 79 of the 1 st turbine blade 45a on the 1 st seal plate 78 side and the inner wall 54 of the 1 st pump casing 16 a.
As shown in fig. 4, the 2 nd impeller 6b as another impeller includes: a 2 nd impeller hub portion 39b fixed to the rotary shaft 2; and a 2 nd impeller wing 45b connected to the 2 nd impeller hub 39 b. The 2 nd impeller hub portion 39b is provided with an annular 2 nd impeller hub portion projecting piece 51b extending in the axial direction toward the stator shield 9 side.
A 2 nd inlet port 58 is provided in a side surface of the 2 nd pump casing 16b in which the 2 nd impeller 6b is housed. The 2 nd inflow port 58 is cylindrical having a central axis coaxial with the rotary shaft 2, and allows the liquid fed from the 1 st impeller 6a to flow in. Further, a discharge port 61 for discharging the liquid flowing into the 2 nd pump casing 16b to the outside of the 2 nd pump casing 16b is provided on the upper surface side of the 2 nd pump casing 16 b.
The 2 nd casing-side bearing housing 32b has a 2 nd communication path 71 that communicates the 2 nd impeller accommodation space 14b and the inner space 66 of the stator shield 9. The 2 nd communication path opening 69 of the 2 nd communication path 71 is located on the wall surface 68 of the 2 nd impeller housing space 14b on the stator shield case 9 side, and is provided in the vicinity of the 2 nd impeller hub through hole 49b at a position closer to the rotating shaft 2 than the 2 nd impeller hub protrusion piece 51b.
The 2 nd casing-side bearing housing 32b forms the 2 nd impeller accommodation space 14b together with the 2 nd pump casing 16 b. The 2 nd casing-side bearing housing 32b has a 2 nd recess 53b on a wall surface 68 on the stator shield 9 side forming the 2 nd impeller housing space 14b. The 2 nd impeller hub protrusion piece 51b provided in the 2 nd impeller hub 39b is inserted into the 2 nd recess 53b.
Further, the 2 nd impeller wing 45b is provided with a cylindrical 2 nd stopper plate 82 coaxially centered with the rotation shaft 2. The 2 nd seal plate 82 extends in the axial direction of the rotary shaft 2 in the direction of the 2 nd inflow port 58, and reduces the gap between the outer peripheral surface thereof and the inner wall 81 of the 2 nd inflow port 58 in the 2 nd pump housing 16 b. The 2 nd seal plate 82 seals between the space in the 2 nd inflow port 58 and the space formed by the outer wall 83 of the 2 nd impeller wing 45b on the 2 nd seal plate 82 side and the inner wall 59 of the 2 nd pump casing 16 b.
The 1 st pump casing 16a and the 2 nd pump casing 16b are connected by a connecting pipe 62 forming a flow path when the liquid is transferred from the 1 st impeller 6a to the 2 nd impeller 6 b. The connecting pipe 62 passes through the outside of the motor frame 18, and feeds the liquid discharged from the liquid supply port 57 of the 1 st pump casing 16a to the 2 nd inlet port 58 of the 2 nd pump casing 16 b.
In the canned motor pump 8 of the present embodiment, as shown in fig. 3 and 4, a part of the liquid transported by the rotation of the impellers 6a and 6b flows between the rotating shaft 2 and the bearings 3a and 3b as indicated by the two-dot chain arrows.
The liquid flowing into the 1 st pump casing 16a from the 1 st inflow port 56 passes through the 1 st impeller vane inner flow path 72 of the 1 st impeller 6a by the rotational force of the 1 st impeller 6a, passes through the connecting pipe 62, and flows into the 2 nd pump casing 16b from the 2 nd inflow port 58.
The liquid flowing into the 2 nd pump casing 16b is branched into two directions, and the branched liquid is discharged from the discharge port 61 to the outside of the 2 nd pump casing 16b through the 2 nd impeller vane inner flow path 73 of the 2 nd impeller 6b by the rotational force of the 2 nd impeller 6 b. The other branched liquid is fed into the stator shield 9 through the 2 nd impeller hub portion through hole 49b of the 2 nd impeller 6 b.
The liquid fed from the 2 nd pump housing 16b into the stator shield 9 is further branched into two directions. The branched liquid passes through the 2 nd communication path 71 provided in the 2 nd pump housing 16b, and passes through the space between the stator shield 9 and the rotor 12 in the direction of the 1 st bearing 3a. The liquid on the other side branched passes between the sleeve 25 of the rotary shaft 2 and the 2 nd bearing 3b.
The liquid passing between the sleeve 25 of the rotary shaft 2 and the 2 nd bearing 3b passes between the 2 nd bearing 3b and the 2 nd supported member 4b, and passes through the space between the stator shield 9 and the rotor 12 in the direction of the 1 st bearing 3a. In the case where the liquid passes between the sleeve 25 of the rotary shaft 2 and the 2 nd bearing 3b and in the case where the liquid passes between the 2 nd bearing 3b and the 2 nd supported member 4b, the liquid mainly passes through the grooves 76, 74 formed in the 2 nd bearing 3b. When the liquid passes between the sleeve 25 of the rotary shaft 2 and the 2 nd bearing 3b and between the 2 nd bearing 3b and the 2 nd supported member 4b, the liquid becomes a lubricant between the sleeve 25 of the rotary shaft 2 and the 2 nd bearing 3b and between the 2 nd bearing 3b and the 2 nd supported member 4b.
The liquid passing through the space between the stator shield 9 and the rotor 12 branches into two directions. The liquid on one side enters the 1 st vane inner channel 72 of the 1 st impeller 6a through the 1 st communication channel 67 of the 1 st pump casing 16a and the 1 st impeller hub portion through hole 49a of the 1 st impeller hub portion 39 a. The other side liquid passes between the 1 st bearing 3a and the 1 st supported bearing member 4a, and passes between the 1 st bearing 3a and the sleeve 25 of the rotary shaft 2. In the case where the liquid passes between the 1 st bearing 3a and the 1 st supported bearing member 4a and in the case where the liquid passes between the 1 st bearing 3a and the sleeve 25 of the rotary shaft 2, the liquid mainly passes through the grooves 74, 76 formed in the 1 st bearing 3a. When the liquid passes between the 1 st bearing 3a and the 1 st supported bearing member 4a and between the 1 st bearing 3a and the sleeve 25 of the rotary shaft 2, the liquid becomes a lubricant between the 1 st bearing 3a and the 1 st supported bearing member 4a and between the 1 st bearing 3a and the sleeve 25 of the rotary shaft 2. The liquid passing between the 1 st bearing 3a and the sleeve 25 of the rotary shaft 2 passes through the 1 st impeller hub portion through hole 49a of the 1 st impeller hub portion 39a and enters the 1 st impeller vane inner passage 72 of the 1 st impeller 6 a.
As shown in fig. 5, the 1 st pump casing 16a and the connecting pipe 62 are connected via a 1 st discharge channel 84 provided on the secondary side of the liquid supply port 57 on the upper surface side of the 1 st pump casing 16 a. The 1 st discharge channel 84 and the connecting pipe 62 are connected by fastening flanges 86 and 87 provided at the opposite ends, respectively, to each other with bolts.
The 2 nd pump casing 16b is connected to the connecting pipe 62 via a 2 nd intake passage 88 provided on the primary side of the 2 nd inflow port 58 of the 2 nd pump casing 16 b. The 2 nd suction channel 88 and the connecting pipe 62 are connected by fastening flanges 89 and 91 provided at the opposite ends, respectively, to each other by bolts.
As shown in fig. 6, 7, and 8, when the bearings 3a and 3B are pressed by the supported members 4a and 4B to the opposite side of the rotor 12 of the motor 11, the elastic structure 7 (7A, 7B, and 7C) imparts an elastic reaction force to one or both of the bearings 3a and 3B and the supported members 4a and 4B in the axial direction.
The rotary shaft 2 moves toward the 1 st impeller 6a by an amount corresponding to the play due to the pressure difference in the axial direction, and the bearings 3a and 3b are pressed against the supported members 4a and 4b in the axial direction. At this time, even if there is a dimensional error in the inner peripheral surfaces of the bearing-supported member housing 38a and the bearing-supported member housing 38b and the inner peripheral surfaces of the casing-side bearing housing 32a and the casing-side bearing housing 32b, the elastic structure 7 is provided, and therefore the bearings 3a, 3b and/or the bearing-supported member 4a and the bearing-supported member 4b come into contact with each other while being inclined at a slight angle with respect to the axial direction so that the surfaces facing each other are in surface contact. In this way, the bearings 3a and 3b are in surface contact with the supported members 4a and 4b, and wear due to the single-side contact between the bearings 3a and 3b and the supported members 4a and 4b is prevented.
Fig. 6 shows an example in which the elastic structure 7B is made of an elastic body provided between the housing-side bearing housing 32a and the opposite side of the bearing 3a from the rotor 12 of the motor 11, and an example in which the elastic structure 7B is provided between the bearing-supported member housing 38a and the side of the bearing-supported member 4a closer to the rotor 12 of the motor 11. The elastic body shown in fig. 6 is a coil spring. The diameter of the coil spring is the same as or smaller than the thicknesses of the bearing 3a and the supported member 4a in the radial direction. The coil springs are provided in plural at a constant interval in the circumferential direction of each of the bearing 3a and the supported member 4a. Fig. 6 shows only the elastic structure 7B on the 1 st impeller 6a side, and the elastic structure 7B on the 2 nd impeller 6B side is omitted. The elastic structure 7B (not shown) on the 2 nd impeller 6B side has a structure symmetrical in the axial direction with the elastic structure 7B on the 1 st impeller 6a side about the rotor 12.
The elastic structure 7C shown in fig. 8 is formed by replacing 1 coil spring with a plurality of coil springs constituting the elastic structure 7B in the example shown in fig. 6. The coil spring constituting the elastic structure 7C is disposed at a concentric position with the rotation shaft 2. The coil springs in fig. 8 press the bearing 3a, the bearing 3b, and the bearing-supported members 4a, 4b near the radial centers of the end surfaces thereof. Fig. 8 shows only the elastic structure 7C on the 1 st impeller 6a side, and the elastic structure 7C on the 2 nd impeller 6b side is omitted. The elastic structure 7C (not shown) on the 2 nd impeller 6b side has a structure symmetrical in the axial direction with the elastic structure 7C on the 1 st impeller 6a side about the rotor 12.
In addition, a spring washer, a belleville washer, a wave washer, or the like may be used instead of the coil springs constituting the elastic structures 7B and 7C.
In the elastic structure 7A of fig. 7, a plate 92 is provided between the housing-side bearing housing 32a and the opposite side of the bearing 3a from the rotor 12 of the motor 11, and the housing-side bearing housing 32a supports only a part of the surface of the plate 92 opposite to the bearing 3a in the axial direction, thereby imparting an elastic reaction force to the bearing 3a in the axial direction. For example, a thin metal plate, such as a metal gasket, can be used as the plate 92. In this case, a bearing-side gap 93 is formed between the casing-side bearing housing 32a and the plate 92. Fig. 7 also highlights the bending of the plate 92 and the inclination of the bearing 3a and the supported member 4a. Fig. 7 shows only the elastic structure 7A on the 1 st impeller 6a side. As shown in fig. 2, the elastic structure 7A on the 2 nd impeller 6b side has a structure symmetrical to the elastic structure 7A on the 1 st impeller 6a side in the axial direction about the rotor 12.
In the present embodiment, the bearing-side gap 93 is formed on one side of the inner diameter side of the plate 92, and the outer diameter side of the plate 92 is sandwiched between the bearing 3a and the bearing 3b and between the housing-side bearing housing 32a and the housing-side bearing housing 32b. Since the bearing-side gap 93 is formed only on one side of the inner diameter side of the plate 92, when the bearings 3a and 3b are inclined with respect to the rotary shaft 2, the plate 92 flexes toward the bearing-side gap 93 side to generate an elastic force.
In fig. 7, as a further elastic structure 7D, the following elastic structure is shown: a plate 92 is provided between the side of the supported member 4a against the rotor 12 of the motor 11 and the supported member housing 38a, and the supported member housing 38a supports only a part of the surface of the plate 92 on the opposite side to the supported member 4a in the axial direction, thereby imparting an elastic reaction force to the supported member 4a in the axial direction. Here, the plate 92 may be made of a thin metal plate, for example, a metal gasket, or the like, and a supported member side gap 94 may be formed between the supported member housing 38a and the plate 92. Fig. 7 shows only the elastic structure 7D on the 1 st impeller 6a side. As shown in fig. 4, the elastic structure 7D on the 2 nd impeller 6b side has a structure symmetrical to the elastic structure 7D on the 1 st impeller 6a side in the axial direction about the rotor 12.
In the present embodiment, the supported member side gap 94 is formed on one surface side of the outer diameter side of the plate 92, and the inner diameter side of the plate 92 is sandwiched by the supported member 4a, the supported member 4b, the supported member housing 38a, and the supported member housing 38b. The supported member side gap 94 is formed only on one surface side of the outer diameter side of the plate 92, and when the supported member 4a and the supported member 4b are inclined with respect to the rotation shaft 2, the plate 92 is deflected toward the supported member side gap 94 side, and an elastic force is generated.
Fig. 9 is a view showing a state in which the bearing 3a and the supported member 4a are in contact with each other with their surfaces slightly inclined with respect to the rotation shaft 2. However, only the bending of the plate 92 is emphasized, and the inclination of the bearing 3a and the supported member 4a is not emphasized.
Since the plate 92 is deflectable toward the bearing-side gap 93 or the supported-member-side gap 94 at any position in the circumferential direction, if the bearings 3a, 3b and the supported-member 4a, 4b are pressed in the axial direction in a state where the bearings 3a, 3b and the supported-member 4a, 4b are not in surface contact with each other, as shown in fig. 9, the portions of the plate 92 deflect toward the bearing-side gap 93 or the supported-member-side gap 94 while the bearings 3a, 3b and the supported-member 4a, 4b are tilted with respect to the axial direction, respectively, and as a result, the bearings 3a, 3b and the supported-member 4a, 4b are in surface contact with each other. In the example shown in fig. 9, the plate 92 is pressed toward the bearing support member side gap 94 by the outer diameter side of the upper part in the drawing of the bearing support member 4a, and the plate 92 is pressed toward the bearing side gap 93 by the inner diameter side of the upper part in the drawing of the bearing 3a, so that each plate 92 is deflected.
As a modification of the above embodiment, in the above embodiment, the plate 92 may be provided only between the bearing 3a and the bearing 3b and the housing-side bearing housing 32a and the housing-side bearing housing 32b, or between the supported member 4a and the supported member 4b and the bearing-side member housing 38a and the supported member housing 38b.
The present invention can be embodied in other various forms without departing from its spirit, spirit or essential characteristics. Accordingly, the above embodiments are merely examples in all respects, and are not to be construed as limiting.
Industrial applicability
The present invention can be applied to, for example, a canned motor pump.
Description of the reference numerals
1. Bearing structure of the shielding electric pump; 2. a rotation shaft; 3a, 3b, bearings; 4a, 4b, supported members; 6a, 6b, impellers; 7A, 7B, 7C, 7D, resilient construction; 8. shielding the electric pump; 11. a motor section; 12. a rotor; 31. a pump section; 32a, 32b, and a casing-side bearing housing; 33. an elastic sheet material; 38a, 38b, a housing for a supported member; 92. a sheet material.
Claims (5)
1. A bearing structure of a canned motor pump is characterized in that,
the bearing structure of the canned motor pump comprises:
a rotation shaft that rotates integrally with a rotor of the motor unit;
a bearing which is fitted into a casing-side bearing housing provided in the pump section via an elastic thin plate material and rotatably supports the rotary shaft in a direction perpendicular to the axial direction;
a supported member mounted on the rotary shaft between the bearing and the rotor of the motor unit, and rotatably supported by the bearing in an axial direction; and
an impeller integrally rotated with the rotation shaft,
in a canned motor pump in which a part of the liquid supplied by the rotation of the impeller flows between the rotation shaft and the bearing,
the bearing structure of the canned motor pump is provided with the following elastic structure: when the bearing is pressed by the supported member to the side opposite to the rotor of the motor, an elastic reaction force is applied to one or both of the bearing and the supported member in the axial direction.
2. The bearing structure of a canned motor pump according to claim 1, wherein,
the elastic structure is an elastic body provided between the housing-side bearing housing and a side of the bearing opposite to the rotor of the motor unit, and imparts the elastic reaction force to the bearing in an axial direction.
3. The bearing structure of a canned motor pump according to claim 1, wherein,
the supported member is attached to the rotary shaft via a housing for the supported member,
the elastic structure is an elastic body provided between the housing for the supported member and a side of the supported member, which is closer to the rotor of the motor unit, and imparts the elastic reaction force to the supported member in the axial direction.
4. The bearing structure of a canned motor pump according to claim 1, wherein,
in the case of the construction of the spring,
a plate material is provided between the housing-side bearing housing and a side of the bearing opposite to the rotor of the motor portion,
only a part of the surface of the plate material on the opposite side of the bearing is supported in the axial direction by the housing-side bearing housing, so that the elastic reaction force is imparted to the bearing in the axial direction.
5. The bearing structure of a canned motor pump according to claim 1, wherein,
the supported member is fixed to the rotary shaft in the axial direction by means of a housing for the supported member,
in the case of the construction of the spring,
a plate material is provided between the side of the supported member against the rotor of the motor unit and the housing for the supported member,
the elastic reaction force is imparted to the supported member in the axial direction by the supported member housing supporting only a part of a surface of the plate material on the opposite side to the supported member in the axial direction.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2021094287 | 2021-06-04 | ||
| JP2021-094287 | 2021-06-04 | ||
| PCT/JP2022/016912 WO2022254959A1 (en) | 2021-06-04 | 2022-03-31 | Canned-motor-pump bearing structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117460892A true CN117460892A (en) | 2024-01-26 |
Family
ID=84323118
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202280039152.5A Pending CN117460892A (en) | 2021-06-04 | 2022-03-31 | Bearing structure of shielding electric pump |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP7525739B2 (en) |
| KR (1) | KR20240004667A (en) |
| CN (1) | CN117460892A (en) |
| WO (1) | WO2022254959A1 (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1169704A (en) * | 1997-08-21 | 1999-03-09 | Asmo Co Ltd | Bearing device for motor |
| JP3897931B2 (en) | 1999-05-20 | 2007-03-28 | 株式会社荏原製作所 | Canned motor pump |
| JP2011032923A (en) * | 2009-07-31 | 2011-02-17 | Yamada Seisakusho Co Ltd | Water pump |
| DE102013208460A1 (en) | 2013-05-08 | 2014-11-13 | Ksb Aktiengesellschaft | Pump arrangement with a sliding bearing arrangement |
| CN116583672A (en) | 2020-12-15 | 2023-08-11 | 三相电机株式会社 | Shielding electric pump |
-
2022
- 2022-03-31 KR KR1020237040864A patent/KR20240004667A/en unknown
- 2022-03-31 JP JP2023525643A patent/JP7525739B2/en active Active
- 2022-03-31 CN CN202280039152.5A patent/CN117460892A/en active Pending
- 2022-03-31 WO PCT/JP2022/016912 patent/WO2022254959A1/en active Application Filing
Also Published As
| Publication number | Publication date |
|---|---|
| JP7525739B2 (en) | 2024-07-30 |
| JPWO2022254959A1 (en) | 2022-12-08 |
| WO2022254959A1 (en) | 2022-12-08 |
| KR20240004667A (en) | 2024-01-11 |
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