CN117759535A

CN117759535A - Spherical rotor pump and tooth cleaning device

Info

Publication number: CN117759535A
Application number: CN202410141398.4A
Authority: CN
Inventors: 吴碧涛; 刘仕华; 请求不公布姓名
Original assignee: Guangzhou Stars Pulse Co Ltd
Current assignee: Guangzhou Stars Pulse Co Ltd
Priority date: 2024-01-31
Filing date: 2024-01-31
Publication date: 2024-03-26

Abstract

The application provides a spherical rotor pump and tooth belt cleaning device. The spherical rotor pump includes: the pump shell is provided with a containing cavity and a mounting cavity, the containing cavity and the mounting cavity are separated by a partition board, and the partition board is provided with a through hole; the rotor assembly comprises a driving rotor and a driven rotor, the driving rotor and the driven rotor are both positioned in the accommodating cavity, the driving rotor, the driven rotor and the wall surface of the accommodating cavity jointly define a variable-volume cavity, the driving rotor can drive the driven rotor to rotate, and when the driving rotor drives the driven rotor to rotate, the volume of the variable-volume cavity changes; the transmission shaft penetrates through the through hole, one part of the transmission shaft is positioned in the mounting cavity, and the other part of the transmission shaft extends into the accommodating cavity and is connected with the driving rotor; and the sealing ring is used for sealing a gap between the transmission shaft and the hole wall of the through hole or sealing a gap between the transmission shaft and the inner wall of the mounting cavity. In this way, the risk of liquid spilling from the drive shaft area can be reduced.

Description

Spherical rotor pump and tooth cleaning device

Technical Field

The application relates to the technical field of oral cavity cleaning, in particular to a spherical rotor pump and a tooth cleaning device.

Background

A spherical rotor pump is a positive displacement liquid feeding device, and generally includes a pump housing and a rotor assembly disposed in the pump housing, and the function of pumping water can be achieved by rotation of the rotor assembly. When the spherical rotor pump works, the rotor assembly in the pump shell rotates at a high speed, and the precise matching of the rotor assembly and the pump shell is a necessary condition for the clearance seal in the pump, so that the parts of the spherical rotor pump usually adopt a precise manufacturing processing mode.

However, the precision manufacturing method also has problems of complicated process, long manufacturing cycle, high cost, and the like. Some manufacturers change part of parts into moulds for batch manufacturing, thereby simplifying the working procedures, improving the production efficiency and reducing the cost, but the phenomenon of gap sealing failure in the inter-pump is easy to occur because the precision of the parts is reduced to some extent. When the clearance seal fails, liquid in the pump is easy to overflow from the transmission shaft part in the process of moving the rotor assembly relative to the pump shell, and the condition of liquid leakage occurs.

Disclosure of Invention

The application provides a spherical rotor pump and tooth cleaning device, aims at reducing the risk that liquid in the pump overflows from the transmission shaft position. The specific technical scheme is as follows:

In a first aspect, the present application provides a spherical rotary pump comprising: the pump comprises a pump shell, a pump body and a control device, wherein the pump shell is provided with a containing cavity and a mounting cavity, the containing cavity and the mounting cavity are separated by a partition board, and the partition board is provided with a through hole; the rotor assembly comprises a driving rotor and a driven rotor, the driving rotor and the driven rotor are both positioned in the accommodating cavity, the wall surfaces of the driving rotor, the driven rotor and the accommodating cavity jointly define a variable-volume cavity, the driving rotor can drive the driven rotor to rotate, and when the driving rotor drives the driven rotor to rotate, the volume of the variable-volume cavity changes; the transmission shaft penetrates through the through hole, one part of the transmission shaft is positioned in the mounting cavity, and the other part of the transmission shaft extends into the accommodating cavity and is connected with the driving rotor; and the sealing ring is used for sealing a gap between the transmission shaft and the hole wall of the through hole or sealing a gap between the transmission shaft and the inner wall of the mounting cavity.

The spherical rotor pump in this application embodiment, the casing has holds chamber and installation cavity, holds chamber and installation cavity and separates through the baffle, and rotor subassembly is located and holds the intracavity, and the through-hole on the baffle is worn to locate by the transmission shaft to with hold the initiative rotor connection in the intracavity. The spherical rotor pump is also provided with a sealing ring, and the sealing ring is used for sealing a gap between the transmission shaft and the hole wall of the through hole or sealing a gap between the transmission shaft and the inner wall of the installation cavity. In this way, even if a problem of failure of the gap seal occurs between the rotor assembly and the inner wall of the receiving chamber, the risk of liquid spilling from the drive shaft portion can be reduced.

In some embodiments, the sealing ring is disposed in the mounting cavity, and the sealing ring is sleeved on the transmission shaft and abuts against the partition plate.

In some embodiments, the spherical rotor pump further comprises: the bearing is positioned in the mounting cavity, the bearing is sleeved on the transmission shaft, the bearing is arranged on one side of the sealing ring away from the partition plate, and the bearing is in contact with the wall surface of the mounting cavity; and a spacer located between the bearing and the seal ring.

In some embodiments, the mounting cavity includes a first section and a second section in communication with each other, the second section being located on a side of the first section remote from the bulkhead; the cross-sectional area of the second section is larger than that of the first section, so that a step-shaped limiting surface is formed at the connecting position of the second section and the first section, the sealing ring is positioned on the first section, the bearing and the separator are both positioned on the second section, and the separator is propped against the limiting surface.

In some embodiments, the spacer is tightly abutted against the sealing ring so that the sealing ring is compressed along the axial direction of the transmission shaft; wherein, before the sealing ring is not compressed, the dimension of the sealing ring along the axial direction of the transmission shaft is larger than the dimension of the first section along the axial direction of the transmission shaft.

In some embodiments, the bearing comprises a bearing inner ring and a bearing outer ring connected with the bearing inner ring, and the bearing inner ring is tightly sleeved on the transmission shaft; the spacer is an annular spacer having an inner diameter greater than an outer diameter of the bearing inner race such that the spacer and the bearing inner race are radially spaced apart.

In some embodiments, the bearing comprises a bearing inner ring and a bearing outer ring connected with the bearing inner ring, and the bearing inner ring is tightly sleeved on the transmission shaft; the spacer is an annular spacer, the inner diameter of the spacer is smaller than the outer diameter of the bearing inner ring, an avoidance gap is formed on one side, close to the bearing, of the spacer, and the avoidance gap is arranged opposite to the bearing inner ring so as to avoid the bearing inner ring.

In some embodiments, the sealing ring is disposed in the accommodating cavity, and the sealing ring is sleeved on the transmission shaft and abuts against the partition plate.

In some embodiments, a first seating groove is provided in the receiving chamber, and the sealing ring is positioned in the first seating groove.

In some embodiments, the spherical rotor pump further comprises an anti-wear gasket disposed between the active rotor and the seal ring.

In some embodiments, a second seating groove is further disposed in the receiving cavity, the second seating groove is in communication with the first seating groove, a portion of the wear pad structure is located in the second seating groove, and a radial dimension of the first seating groove is smaller than a radial dimension of the second seating groove.

In some embodiments, the thickness of the wear pad is greater than the depth of the second seating groove such that a portion of the wear pad structure protrudes beyond the second seating groove.

In some embodiments, the rotor assembly comprises a driving rotor and a driven rotor, both of which are located in the accommodation chamber, the transmission shaft being connected to the driving rotor; the anti-abrasion wear-resistant device is characterized in that a limiting end face is arranged at one end, close to the anti-abrasion gasket, of the driving rotor, the limiting end face is a plane, and the limiting end face abuts against the anti-abrasion gasket.

In some embodiments, a limit part is formed at one end of the driving rotor, which is far away from the driven rotor, and the limit end surface is formed at the limit part; the accommodating cavity is internally provided with a third accommodating groove, the third accommodating groove is communicated with the second accommodating groove, the limiting part is positioned in the third accommodating groove, and the radial size of the second accommodating groove is smaller than that of the third accommodating groove.

In some embodiments, the wear pad is tightly abutted against the seal ring so that the seal ring is compressed along the axial direction of the transmission shaft; before the sealing ring is not compressed, the dimension of the sealing ring along the axial direction of the transmission shaft is larger than the dimension of the first placement groove along the axial direction of the transmission shaft.

In some embodiments, the seal ring is a Y-shaped seal ring, the Y-shaped seal ring comprising a seal ring body, one side of the seal ring body being provided with an inner lip and an outer lip, the inner lip and the outer lip abutting the bulkhead.

In some embodiments, the pump housing comprises a first housing and a second housing, the first housing and the second housing being connected, the first housing and the second housing together defining the receiving cavity, the second housing defining the mounting cavity; the spherical rotor pump further comprises a driving device, the driving device comprises a main body part and an output shaft connected with the main body part, the main body part is connected with the second shell, and the output shaft is positioned in the mounting cavity and connected with the transmission shaft; the spherical rotor pump further comprises a bearing, the bearing is positioned in the mounting cavity, the bearing is sleeved on the transmission shaft and/or the output shaft, the bearing is arranged on one side, far away from the partition plate, of the sealing ring, and the bearing is in contact with the wall surface of the mounting cavity; the spherical rotor pump further comprises a supporting block, the supporting block is arranged on one side, away from the partition plate, of the bearing, and the supporting block is fixed in the installation cavity.

In some embodiments, the main body portion has an end face disposed toward the pump housing, the end face being formed with a raised structure, the raised structure being located within the mounting cavity, the support block being against the raised structure; the radial dimension of the supporting block is larger than the radial dimension of the protruding structure.

In some embodiments, the driving rotor includes a first supporting member and a first covering body, the first supporting member is wrapped inside the first covering body to serve as an inner skeleton of the driving rotor, and the transmission shaft extends into the first covering body and is connected with the first supporting member, wherein the transmission shaft is fixedly connected with the first supporting member, or the transmission shaft and the first supporting member are in an integrated structure; and/or the driven rotor comprises a second support and a second encapsulant covering at least part of the second support.

In some embodiments, the spherical rotor pump further comprises a limit structure disposed between the drive shaft and the pump housing, the limit structure being configured to limit movement of the drive shaft relative to the pump housing in a direction of its own axis.

In some embodiments, the pump housing is formed with a stop surface; the limiting structure comprises a first member, a second member and a gasket, wherein the first member is connected with the transmission shaft, so that the first member is fixed relative to the transmission shaft along the axial direction of the transmission shaft, the second member is fixedly connected with the pump shell, the gasket is abutted to the limiting surface, and the first member is limited between the gasket and the second member.

In some embodiments, the first member is a bearing sleeved on the drive shaft; the bearing comprises a bearing outer ring and a bearing inner ring connected with the bearing outer ring, the bearing inner ring is fastened on the transmission shaft, one end of the bearing outer ring is abutted against the gasket, and the other end of the bearing outer ring is abutted against the second component.

In some embodiments, the limiting structure further comprises a third member fixedly connected with the transmission shaft, and the third member abuts against one end, away from the gasket, of the bearing inner ring.

In some embodiments, the third component is a clamp spring sleeved on the transmission shaft or a pin fixedly mounted on the transmission shaft.

In some embodiments, the first member is a clamp spring sleeved on the transmission shaft, or the first member is a pin fixedly mounted on the transmission shaft.

In some embodiments, the second member is a snap ring that is interference fit with the mounting cavity.

In some embodiments, the driving rotor and the driven rotor are connected by a pin.

In some embodiments, the active rotor includes a first support and a first encapsulant, a portion of the first support is wrapped inside the first encapsulant to serve as an inner skeleton of the active rotor, and another portion of the first support is located outside the first encapsulant to form a connection; the driven rotor comprises a second supporting piece and a second wrapping body, the second wrapping body covers at least part of the second supporting piece, a through groove is formed in the second wrapping body, and the connecting portion extends into the second wrapping body through the through groove and is connected with the second supporting piece through the pin shaft.

In some embodiments, the width of the through groove is greater than the width of the connecting portion such that there is a space between the connecting portion and the side wall of the through groove. 30. The spherical rotor pump of claim 27 wherein the driving rotor has a first axis about which the driving rotor is rotatable relative to the pump housing, the driven rotor has a second axis about which the driven rotor is rotatable relative to the pump housing, the first axis intersecting the second axis; the driven rotor is provided with a groove, the driving rotor is provided with a pin shaft part, the surface of the pin shaft part is a cylindrical surface or a semi-cylindrical surface, and the pin shaft part is limited in the groove and can rotate around a third axis relative to the groove; the central axis of the pin shaft coincides with the third axis.

In some embodiments, the spherical rotor pump further comprises a drive device and a constraint structure, the drive device having an output shaft capable of rotating the drive shaft; the restraining structure is sleeved on the output shaft and the transmission shaft so that the output shaft and the transmission shaft are kept fixed.

In some embodiments, the output shaft and the constraining structure are both located within the mounting cavity, a portion of the drive shaft is located within the mounting cavity, and another portion of the drive shaft extends into the receiving cavity; the restraining structure is a sleeve, and a space is reserved between the outer wall surface of the sleeve and the wall surface of the mounting cavity.

In some embodiments, the output shaft and the constraining structure are both located within a mounting cavity, a portion of the drive shaft is located within the mounting cavity, and another portion of the drive shaft extends into the receiving cavity; the restraining structure is a bearing, the bearing is positioned in the mounting cavity, and the outer wall surface of the bearing is contacted with the wall surface of the mounting cavity.

In some embodiments, the drive device further comprises a body portion, the output shaft being connected to the body portion; the mounting cavity is internally provided with a limiting surface, the spherical rotor pump further comprises a supporting block, the supporting block is positioned in the mounting cavity and is abutted to the main body part, and the bearing is limited between the limiting surface and the supporting block.

In some embodiments, the output shaft comprises a first mating portion provided with a first contact surface, and the drive shaft comprises a second mating portion provided with a second contact surface, the first contact surface being in close abutment with the second contact surface to enable torque transfer between the output shaft and the drive shaft.

In some embodiments, the first contact surface and the second contact surface are both planar.

In some embodiments, the first mating portion has a cross-sectional shape that is a first semicircle and the second mating portion has a cross-sectional shape that is a second semicircle, the radius of the first semicircle being equal to the radius of the second semicircle.

In some embodiments, the output shaft includes a third mating portion, the drive shaft includes a fourth mating portion, one of the third mating portion and the fourth mating portion is a prismatic structure, the other of the third mating portion and the fourth mating portion is a mounting sleeve having an inner cavity shaped to mate with the prismatic structure, the prismatic structure mated to the inner cavity.

In some embodiments, one of the output shaft and the drive shaft is provided with a clamping groove, and the other of the output shaft and the drive shaft is provided with a flat shaft portion, the flat shaft portion being engaged with the clamping groove to enable torque transmission between the output shaft and the drive shaft.

In some embodiments, one of the output shaft and the drive shaft is further provided with a mounting hole extending in an axial direction, and the other of the output shaft and the drive shaft is further provided with a mounting portion connected with the flat shaft portion, the mounting portion being interference fit with the mounting hole.

In some embodiments, the spherical rotor pump further comprises a seal; the pump shell comprises a first shell and a second shell connected with the first shell, the first shell and the second shell jointly define the containing cavity, and the sealing piece is positioned between the first shell and the second shell and surrounds the containing cavity; one of the first shell and the second shell is provided with a groove, the other one of the first shell and the second shell is provided with a protrusion, the protrusion stretches into the groove, and the end face of the protrusion abuts against the sealing element so as to press the sealing element into the groove.

In some embodiments, the thickness of the protrusions decreases gradually in a direction away from the rotor assembly.

In some embodiments, the protrusions are annular structures and the cross-sectional shape of the protrusions is trapezoidal.

In some embodiments, the drive rotor has a first axis about which the drive rotor is rotatable relative to the pump housing; the driven rotor having a second axis about which the driven rotor is rotatable relative to the pump housing, the first axis intersecting the second axis; the end face of the protrusion is perpendicular to the second axis, or an included angle between the end face of the protrusion and the second axis is greater than 90 ° and less than or equal to 135 °.

In some embodiments, the groove includes a first portion and a second portion in communication with each other, the second portion being located on a side of the first portion remote from the protrusion, the first portion having a width greater than a width of the second portion, the protrusion being located within the first portion, the seal being located at least within the second portion.

In some embodiments, the first housing and the second housing each include a housing body portion having an open end and a mating portion located outside of the housing body portion and disposed about the open end.

In some embodiments, the abutting portion of the first housing and/or the abutting portion of the second housing is provided with a reinforcing rib.

In some embodiments, the recess is a distance greater than or equal to 0.8mm from a wall of the receiving cavity;

and/or the distance from the groove to the outer surface of the butt joint part is greater than or equal to 0.8mm;

and/or a distance from the bottom of the groove to the surface of the butt joint part in the thickness direction is greater than or equal to 0.8mm;

and/or the width of the protrusion is greater than or equal to 0.8mm.

In some embodiments, the distance of the groove to the outer surface of the docking portion is greater than the distance of the groove to the wall of the receiving cavity.

In some embodiments, the seal is an annular seal, the seal having a circular cross-sectional shape.

In some embodiments, the driven rotor has a second axis about which the driven rotor is rotatable relative to the pump housing; the driving rotor is provided with a first axis, the driving rotor can rotate around the first axis relative to the pump shell, the driven rotor comprises a base part and a pin shaft part arranged on the base part, the driving rotor is provided with a groove, and the pin shaft part is limited in the groove and can rotate around a third axis relative to the groove; the pin shaft part is provided with a first matching surface and side surfaces positioned at two sides of the first matching surface, the first matching surface is connected with the two side surfaces, the first matching surface is an arc-shaped surface, the central angle of the first matching surface is smaller than or equal to 180 degrees, and the minimum distance between the two side surfaces is equal to the chord length of the first matching surface.

In some embodiments, both of the sides are planar and the sides are disposed parallel to each other; alternatively, both of the side surfaces are curved surfaces.

In some embodiments, the two side surfaces are both plane surfaces, and an included angle between a space plane in which one side surface is located and a space plane in which the other side surface is located is greater than 0 ° and less than or equal to 15 °.

In some embodiments, the groove has a second mating surface and a clearance portion located on both sides of the second mating surface, the second mating surface is an arc-shaped surface, the second mating surface is configured to mate with the first mating surface, and a gap is formed between the clearance portion and the pin shaft portion.

In some embodiments, the gap between the clearance portion and the pin portion is gradually reduced in a direction approaching the second mating face.

In some embodiments, the clearance between the clearance portion and the pin portion is greater than or equal to 0.05mm and less than or equal to 0.6mm.

In some embodiments, the base has two first planar portions facing the second rotor, the two first planar portions being located on both sides of the pin shaft portion, the second rotor has two second planar portions facing the base, the two second planar portions being disposed in one-to-one opposition to the two first planar portions; the pin shaft portion, the wall surface of the accommodating cavity, the first plane portion and the corresponding second plane portion jointly define a volume-variable cavity, and the volume of the volume-variable cavity changes in the process that the pin shaft portion rotates around a third axis relative to the groove.

In some embodiments, an end of the clearance portion away from the second mating surface is a first end, an end of the clearance portion close to the second mating surface is a second end, a connection line between the first end and the third axis is a first connection line, a connection line between the second end and the third axis is a second connection line, and a first included angle is formed between the first connection line and the second connection line; one end of the side surface, which is far away from the first matching surface, is a third end, one end of the side surface, which is close to the first matching surface, is a fourth end, a connecting line of the third end and the third axis is a third connecting line, a connecting line of the fourth end and the third axis is a fourth connecting line, and a second included angle is formed between the third connecting line and the fourth connecting line; the first included angle is larger than the second included angle.

In some embodiments, the second included angle is less than 40 °.

In some embodiments, the ball rotor pump has a first state in which the volume of one of the two variable-volume chambers reaches a minimum and the volume of the other of the two variable-volume chambers reaches a maximum; in the first state, the first plane part and the corresponding second plane part in any one of the variable volume cavities are kept at a distance.

In some embodiments, a transition chamfer is formed between the clearance portion and the second planar portion.

In some embodiments, the first mating surface and the second mating surface are made of materials having the same coefficient of expansion.

In some embodiments, the first mating surface and the second mating surface are made of the same material.

In some embodiments, the base further has an outer surface for mating with a wall of the receiving cavity, the outer surface being spherical; the end surfaces of the two ends of the pin shaft part along the third axis direction are spherical surfaces consistent with the outer surfaces.

In a second aspect, the present application provides a tooth cleaning device comprising a spherical rotor pump according to any one of the embodiments described above.

The casing of spherical rotor pump among this application embodiment has holds chamber and installation cavity, holds chamber and installation cavity and separates through the baffle, and rotor subassembly is located and holds the intracavity, and the through-hole on the baffle is worn to locate by the transmission shaft to with hold the intracavity initiative rotor connection. The spherical rotor pump is also provided with a sealing ring, and the sealing ring is used for sealing a gap between the transmission shaft and the hole wall of the through hole or sealing a gap between the transmission shaft and the inner wall of the installation cavity. In this way, even if a problem of failure of the gap seal occurs between the rotor assembly and the inner wall of the receiving chamber, the risk of liquid spilling from the drive shaft portion can be reduced.

Drawings

FIG. 1 is a schematic diagram of a spherical rotor pump according to an embodiment of the present disclosure;

FIG. 2 is a schematic view of a spherical rotary pump according to an embodiment of the present disclosure at another view angle;

FIG. 3 is a schematic cross-sectional view of section A-A of the structure shown in FIG. 2 in one embodiment;

FIG. 4 is a schematic cross-sectional view of section A-A of the structure of FIG. 2 in another embodiment;

FIG. 5 is a schematic view of a spacer according to an embodiment of the present application;

FIG. 6 is a schematic structural diagram of a seal ring according to an embodiment of the present disclosure;

FIG. 7 is a schematic cross-sectional view of a seal ring according to one embodiment of the present disclosure;

FIG. 8 is a schematic structural view of a ball rotor pump according to another embodiment of the present disclosure;

FIG. 9 is a schematic view of a spherical rotary pump according to another embodiment of the present disclosure at another view angle;

FIG. 10 is a schematic cross-sectional view of section B-B of the structure shown in FIG. 7;

FIG. 11 is a schematic cross-sectional view of section A-A of the structure of FIG. 2 in another embodiment;

FIG. 12 is an exploded view of a spherical rotary pump according to an embodiment of the present disclosure;

FIG. 13 is an exploded view of a part of the structure of a spherical rotary pump according to an embodiment of the present application;

FIG. 14 is a schematic view of a rotor assembly according to an embodiment of the present disclosure;

Fig. 15 is a schematic structural view of a driven rotor according to an embodiment of the present disclosure;

FIG. 16 is a schematic structural view of an active rotor according to an embodiment of the present disclosure;

FIG. 17 is a schematic structural view of a rotor assembly according to an embodiment of the present disclosure (the first encapsulant and the second encapsulant are omitted);

FIG. 18 is a schematic cross-sectional view of section A-A of the structure of FIG. 2 in another embodiment;

FIG. 19 is a schematic cross-sectional view of a section B-B of the structure of FIG. 7 in another embodiment;

FIG. 20 is a schematic view of a connection structure between an output shaft and a transmission shaft of a driving device according to an embodiment of the present disclosure;

FIG. 21 is a schematic diagram of a driving device according to an embodiment of the present disclosure;

FIG. 22 is a schematic view of a propeller shaft according to one embodiment of the present disclosure;

fig. 23 is a schematic view of a connection structure between an output shaft and a transmission shaft of a driving device according to another embodiment of the present disclosure;

FIG. 24 is a schematic view of a driving device according to another embodiment of the present disclosure;

FIG. 25 is a schematic view of a propeller shaft provided in another embodiment of the present application;

FIG. 26 is an enlarged schematic view of portion B of FIG. 3;

FIG. 27 is an enlarged partial schematic view of the structure of FIG. 3 (with the seal hidden);

FIG. 28 is an enlarged schematic view of portion C of FIG. 27;

FIG. 29 is an exploded view of a spherical rotary pump according to an embodiment of the present disclosure;

FIG. 30 is a schematic structural view of a first housing according to an embodiment of the present disclosure;

FIG. 31 is an enlarged partial schematic view of FIG. 3;

FIG. 32 is a schematic view of a rotor assembly in an embodiment of the present application;

FIG. 33 is a schematic view of a driven rotor in an embodiment of the present application;

FIG. 34 is a schematic view of a driven rotor according to an embodiment of the present disclosure from another perspective;

FIG. 35 is a schematic view of an active rotor according to an embodiment of the present disclosure;

fig. 36 is a schematic view of a tooth cleaning device according to an embodiment of the present application.

Reference numerals illustrate:

1000. a tooth cleaning device;

100. a spherical rotor pump; 200. a body; 300. a nozzle;

1. a pump housing; 101. a receiving chamber; 102. a mounting cavity; 103. a partition plate; 104. a through hole; 105. a first seating groove; 106. a second seating groove; 107. a first housing; 108. a second housing; 109. a first section; 110. a second section; 111. a limiting surface; 121. a groove; 1211. a first portion; 1212. a second portion; 122. a protrusion; 1221. an end face; 131. a case main body portion; 132. a butt joint part; 133. reinforcing ribs;

2. a rotor assembly; 201. a driving rotor; 202. a driven rotor; 2021. a second planar portion; 203. a variable volume cavity; 204. a first support; 2041. a connection part; 205. a first encapsulant; 206. a second support; 207. a second encapsulant; 2071. a through groove; 208. a pin shaft; 209. a pin shaft portion; 2091. a first mating surface; 2092. a side surface; 2093. a third end; 2094. a fourth end; 2095. an end face; 210. a groove; 2101. a second mating surface; 2102. a clearance part; 2103. a first end; 2104. a second end; 2105. transitional chamfering; 214. a base; 2141. a first planar portion; 2142. an outer surface;

3. A transmission shaft; 301. a second mating portion; 3011. a second contact surface; 302. a clamping groove; 303. a mounting hole;

4. a seal ring; 401. a seal ring body; 402. an inner lip; 403. an outer lip;

5. a driving device; 501 output shaft; 5011. a first mating portion; 5012. a first contact surface; 5013. a flat shaft portion; 5014. a mounting part; 502. a main body portion; 503. an end face; 504. a bump structure;

6. a bearing; 601. a bearing inner ring; 602. a bearing outer ring;

7. a spacer; 701. avoiding the notch;

8. an anti-abrasion gasket;

9. a support block;

10. a limit structure; 1001. a first member; 1002. a second member; 1003. a third member; 1004. a gasket;

12. a clasp;

13. a constraining structure;

14. a sleeve;

16. a seal;

23. a gasket.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the present application will be further described in detail with reference to the accompanying drawings and examples. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the present application.

In the description of the present application, it should be understood that, if there is an azimuth or positional relationship indicated by terms such as "upper", "lower", "left", "right", etc., based on the azimuth or positional relationship shown in the drawings, this is for convenience of description and simplification of the description, but does not indicate or imply that the apparatus or element to be referred must have a specific azimuth, be constructed and operated in a specific azimuth, and thus terms describing the positional relationship in the drawings are merely used for illustration and are not to be construed as limitations of the present patent, and that the specific meaning of the terms described above may be understood by those of ordinary skill in the art according to the specific circumstances.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as implying or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present application, the meaning of "plurality" is at least two, such as two, three, etc., unless explicitly defined otherwise.

In the description of the present application, unless explicitly stated and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrated; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.

Based on this, embodiments of the first aspect of the present application provide a spherical rotor pump aimed at reducing the risk of liquid within the pump overflowing from the drive shaft site.

As shown in fig. 1, 2 and 3, a spherical rotor pump 100 according to an embodiment of the first aspect of the present application includes a pump housing 1, a rotor assembly 2, a transmission shaft 3 and a seal ring 4. The pump housing 1 has a housing chamber 101 and a mounting chamber 102, the housing chamber 101 and the mounting chamber 102 being partitioned by a partition plate 103, the partition plate 103 being provided with a through hole 104. The rotor assembly 2 includes a driving rotor 201 and a driven rotor 202, where the driving rotor 201 and the driven rotor 202 are both located in the accommodating cavity 101, the driving rotor 201, the driven rotor 202 and the wall surface of the accommodating cavity 101 define a variable-volume cavity 203 together, the driving rotor 201 can drive the driven rotor 202 to rotate, and when the driving rotor 201 drives the driven rotor 202 to rotate, the volume of the variable-volume cavity 203 changes. The transmission shaft 3 is arranged through the through hole 104, one part of the transmission shaft 3 is positioned in the mounting cavity 102, and the other part of the transmission shaft 3 extends into the accommodating cavity 101 and is connected with the driving rotor 201. The seal ring 4 is used for sealing a gap between the drive shaft 3 and the wall of the through hole 104 or for sealing a gap between the drive shaft 3 and the inner wall of the installation cavity 102.

Specifically, the transmission shaft 3 is used for being connected with the driving device 5, the driving device 5 can provide power, and the driving device 5 can drive the driving rotor 201 to rotate through the transmission shaft 3 during operation. During the process of driving rotor 201 to drive driven rotor 202 to rotate, the position and volume of variable volume cavity 203 are changed. Typically, the pump casing 1 is provided with a liquid inlet and a liquid outlet, and the same variable volume chamber 203 is alternately communicated with the liquid inlet and the liquid outlet along with the rotation of the rotor assembly 2. And, the volume of the volume-variable cavity 203 when communicating with the liquid inlet is larger than the volume of the volume-variable cavity when communicating with the liquid outlet. Thus, as the variable volume chamber 203 rotates from the position where it communicates with the liquid inlet to the position where it communicates with the liquid outlet, the pressure in the accommodating chamber 101 increases, thereby driving the liquid to be pumped out from the liquid outlet.

In the spherical rotor pump 100 in the embodiment of the application, the housing is provided with a containing cavity 101 and a mounting cavity 102, the containing cavity 101 and the mounting cavity 102 are separated by a partition plate 103, the rotor assembly 2 is located in the containing cavity 101, and the transmission shaft 3 penetrates through a through hole 104 in the partition plate 103 to be connected with the driving rotor 201 in the containing cavity 101. The spherical rotor pump 100 is further provided with a seal ring 4, the seal ring 4 being used to seal a gap between the drive shaft 3 and the wall of the through hole 104 or to seal a gap between the drive shaft 3 and the inner wall of the installation cavity 102. In this way, the risk of liquid spilling from the region of the drive shaft 3 is reduced even if there is a problem of failure of the gap seal between the rotor assembly 2 and the inner wall of the receiving chamber 101.

In some embodiments, as shown in fig. 3, a seal ring 4 is disposed in the mounting cavity 102, and the seal ring 4 is sleeved on the transmission shaft 3. So arranged, the sealing ring 4 seals against the side of the mounting chamber 102 to reduce the risk of spillage of liquid.

Specifically, the seal ring 4 may abut against the partition 103, thereby sealing the gap between the transmission shaft 3 and the through hole 104.

Alternatively, the seal ring 4 may be spaced apart from the partition 103, and in this case, the seal ring 4 may abut against the inner wall of the installation cavity 102, so as to seal the gap between the transmission shaft 3 and the inner wall of the installation cavity 102.

Further, as shown in fig. 3, the spherical rotor pump 100 may further include a bearing 6 and a spacer 7, the bearing 6 is located in the installation cavity 102, the bearing 6 is sleeved on the transmission shaft 3, the bearing 6 is disposed on one side of the sealing ring 4 away from the partition 103, the bearing 6 contacts with a wall surface of the installation cavity 102, and the spacer 7 is located between the bearing 6 and the sealing ring 4. Through setting up the bearing 6 that the cover was located transmission shaft 3 to make bearing 6 and the wall contact of installation cavity 102, can improve the centering precision of transmission shaft 3 when the installation through bearing 6, in addition, drive device 5 drive transmission shaft 3 pivoted in-process, also can guarantee that the position of transmission shaft 3 does not take place the skew, thereby improve transmission shaft 3's position stability. In addition, the bearing 6 and the sealing ring 4 are isolated by the isolating piece 7, so that the sealing ring 4 is not influenced when the bearing 6 moves, and the sealing performance is prevented from being influenced by the displacement of the sealing ring 4.

Further, as shown in fig. 3, the mounting chamber 102 includes a first section 109 and a second section 110 that communicate with each other, the second section 110 being located on a side of the first section 109 remote from the partition 103; the cross-sectional area of the second section 110 is larger than that of the first section 109, so that a stepped limiting surface 111 is formed at the connection position of the second section 110 and the first section 109, the sealing ring 4 is positioned on the first section 109, the bearing 6 and the spacer 7 are both positioned on the second section 110, and the spacer 7 is abutted against the limiting surface 111.

Since the cross-sectional area of the second section 110 of the mounting cavity 102 is larger than that of the first section 109, the sealing ring 4 is positioned in the first section 109 with smaller cross-sectional area, which is beneficial to the compression state of the sealing ring 4, so that the sealing performance can be better exerted. In addition, the connection position of the second section 110 and the first section 109 is a stepped limiting surface 111, and the spacers 7 are located in the second section 110 and the spacers 7 are abutted against the limiting surface 111, so that the spacers 7 can prevent the seals from being separated from the first portion through blocking action of the spacers 7, and on the other hand, excessive extrusion of the spacers 7 on the sealing ring 4 is avoided through limiting action of the limiting surface 111, so that excessive friction force between the sealing ring 4 and the transmission shaft 3 is caused.

Specifically, the spacer 7 tightly abuts against the seal ring 4, so that the seal ring 4 is compressed along the axial direction of the transmission shaft 3; wherein the dimension of the sealing ring 4 in the axial direction of the drive shaft 3 is larger than the dimension of the first section 109 in the axial direction of the drive shaft 3 before the sealing ring 4 is not compressed.

It will be appreciated that the seal ring 4, in the uncompressed condition (in the natural state), has a dimension in the axial direction of the drive shaft 3 which is greater than the dimension of the first section 109 in the axial direction of the drive shaft 3. When the seal ring 4 is mounted on the first section 109, the seal ring 4 is compressed in the axial direction of the transmission shaft 3, and is deformed by extrusion, which is advantageous in improving the sealing performance of the seal ring 4.

In one embodiment, as shown in fig. 3 and 5, the bearing 6 includes a bearing inner ring 601 and a bearing outer ring 602 connected with the bearing inner ring 601, the bearing inner ring 601 is tightly sleeved on the transmission shaft 3, the spacer 7 is an annular spacer, the inner diameter of the spacer is smaller than the outer diameter of the bearing inner ring 601, an avoidance gap 701 is formed on one side of the spacer, which is close to the bearing 6, and the avoidance gap 701 is arranged opposite to the bearing inner ring 601 so as to avoid the bearing inner ring 601.

It will be appreciated that as the drive shaft 3 rotates, the bearing inner race 601 rotates with the drive shaft 3 and the bearing outer race 602 remains stationary. When the spacer 7 is an annular spacer, and the inner diameter of the spacer is smaller than the outer diameter of the bearing inner ring 601, the spacer and the bearing inner ring 601 are not contacted by arranging the avoiding notch 701 on one side of the spacer, which is close to the bearing 6, so that friction occurs between the spacer and the wall bearing inner ring 601 during rotation.

In another embodiment, the bearing 6 includes a bearing inner ring 601 and a bearing outer ring 602 connected to the bearing inner ring 601, the bearing inner ring 601 is fastened and sleeved on the transmission shaft 3, the spacer 7 is an annular spacer, and the inner diameter of the spacer is larger than the outer diameter of the bearing inner ring 601, so that the spacer and the bearing inner ring 601 are spaced apart in the radial direction.

In the case where the spacer 7 is an annular spacer, and the inner diameter of the spacer is larger than the outer diameter of the bearing inner race 601, the spacer and the bearing inner race 601 may be kept in a gap in the radial direction so that the spacer and the bearing inner race 601 do not come into contact. In this way, friction with the spacer during rotation of the bearing inner race 601 can be avoided.

In other embodiments, as shown in fig. 4, the sealing ring 4 is disposed in the accommodating cavity 101, and the sealing ring 4 is sleeved on the transmission shaft 3 and abuts against the partition 103. The arrangement is such that the sealing ring 4, and thus the side of the receiving chamber 101, seals the gap between the drive shaft 3 and the wall of the through hole 104, to reduce the risk of liquid spilling into the mounting chamber 102.

Further, a first seating groove 105 may be provided in the receiving chamber 101, and the sealing ring 4 is positioned in the first seating groove 105. Thereby, the sealing ring 4 is limited by the first mounting groove 105, so that the sealing ring 4 is favorable for maintaining the position stability.

Further, as shown in fig. 4, the spherical rotor pump 100 may further include an anti-wear gasket 8, the anti-wear gasket 8 being disposed between the driving rotor 201 and the seal ring 4. The anti-abrasion gasket 8 separates the sealing ring 4 from the driving rotor 201, so that the problem that the sealing ring 4 is abraded or displaced due to friction with the sealing ring 4 when the driving rotor 201 rotates can be avoided.

Further, a second positioning groove 106 is further arranged in the accommodating cavity 101, the second positioning groove 106 is communicated with the first positioning groove 105, a part of the structure of the wear-resistant gasket 8 is positioned in the second positioning groove 106, and the radial size of the first positioning groove 105 is smaller than that of the second positioning groove 106. So set up, can carry out spacingly through the second mounting groove to the abrasionproof gasket 8, make abrasionproof gasket 8 keep the position stability, in addition, also can utilize abrasionproof gasket 8 to the effect of blockking up of sealing washer 4, make sealing washer 4 remain in first setting groove 105 all the time.

Further, the thickness of the wear pad 8 is greater than the depth of the second seating groove 106 so that a portion of the wear pad 8 structure protrudes beyond the second seating groove 106. In this way, the rotor assembly 2 abuts the portion of the wear pad 8 that extends beyond the second seating groove 106 such that a portion of the wear pad 8 is compressed in the second seating groove 106, and the compressed wear pad 8 compresses the seal ring 4 further in the first seating groove 105. Thus, the seal ring 4 can be tightly abutted against the partition 103, so that the sealing performance of the seal ring 4 can be improved.

Further, as shown in fig. 3 and 4, the rotor assembly 2 includes a driving rotor 201 and a driven rotor 202, both of the driving rotor 201 and the driven rotor 202 are located in the accommodating chamber 101, and the transmission shaft 3 is connected to the driving rotor 201. One end of the driving rotor 201, which is close to the anti-abrasion gasket 8, is provided with a limiting end face, the limiting end face is a plane, and the limiting end face abuts against the anti-abrasion gasket 8. In this embodiment, the end of the driving rotor 201 near the anti-wear pad 8 is provided with a limiting end surface, which is a plane and abuts against the anti-wear pad 8, so that the stress uniformity of the anti-wear pad 8 can be improved.

Further, as shown in fig. 3 and 4, a limit portion 2012 is formed at an end of the driving rotor 201 away from the driven rotor 202, and a limit end face is formed at the limit portion 2012. The accommodating cavity 101 is further provided with a third accommodating groove 141, the third accommodating groove 141 is communicated with the second accommodating groove 106, the limiting part 2012 is positioned in the third accommodating groove 141, and the radial dimension of the second accommodating groove 106 is smaller than that of the third accommodating groove 141. By forming the limiting portion 2012 on the driving rotor 201 and positioning the limiting portion 2012 in the third positioning groove 141, the driving rotor 201 can maintain a preset posture in the accommodating cavity 101, and unexpected rotational movement of the driving rotor is avoided.

In some embodiments, the anti-wear gasket 8 is tightly abutted against the seal ring 4, so that the seal ring 4 is compressed along the axial direction of the transmission shaft 3; wherein, before the seal ring 4 is not compressed, the dimension of the seal ring 4 along the axial direction of the transmission shaft 3 is larger than the dimension of the first seating groove 105 along the axial direction of the transmission shaft 3.

It will be appreciated that the dimension of the seal ring 4 in the axial direction of the drive shaft 3 is larger than the dimension of the first seating groove 105 in the axial direction of the drive shaft 3 in the uncompressed state (in the natural state). When the seal ring 4 is mounted in the first mounting groove 105, the seal ring 4 is compressed in the axial direction of the transmission shaft 3, and is deformed by extrusion, thus being beneficial to improving the sealing performance of the seal ring 4.

In some embodiments, as shown in fig. 6 and 7, the seal ring 4 is a Y-shaped seal ring, the Y-shaped seal ring includes a seal ring body 401, and an inner lip 402 and an outer lip 403 are disposed on one side of the seal ring body 401, where the inner lip 402 and the outer lip 403 abut against the partition 103. When the Y-shaped seal ring 4 is deformed by being pressed, the inner lip 402 and the outer lip 403 deform more than the seal ring body 401. In this embodiment, the inner lip 402 and the outer lip 403 of the sealing ring 4 are abutted against the partition 103, so that the sealing property between the sealing ring 4 and the partition 103 is better, thereby further reducing the possibility of liquid in the accommodating chamber 101 leaking out through the through hole 104.

In some embodiments, the pump housing 1 comprises a first housing 107 and a second housing 108, the first housing 107 and the second housing 108 being connected, the first housing 107 and the second housing 108 together defining the receiving chamber 101, the second housing 108 defining the mounting chamber 102. The spherical rotor pump 100 further comprises a drive device 5, the drive device 5 comprising a body part 502 and an output shaft 501 connected to the body part 502, the body part 502 being connected to the second housing 108, the output shaft 501 being located in the mounting chamber 102 and being connected to the drive shaft 3.

In some embodiments, as shown in fig. 8, 9 and 10, the spherical rotor pump 100 further includes a bearing 6, where the bearing 6 is located in the installation cavity 102, the bearing 6 is sleeved on the transmission shaft 3 and/or the output shaft 501, the bearing 6 is disposed on a side of the sealing ring 4 away from the partition 103, and the bearing 6 contacts a wall surface of the installation cavity 102. The spherical rotor pump 100 further comprises a support block 9, the support block 9 being arranged on the side of the bearing 6 remote from the diaphragm 103, the support block 9 being fixed in the mounting cavity 102.

Wherein, drive arrangement 5 can the motor, and drive arrangement 5's output shaft 501 is located installation cavity 102 and is connected with transmission shaft 3, like this, can form the guard action to output shaft 501 and transmission shaft 3 through installation cavity 102, prevent that outside debris from touching output shaft 501 or transmission shaft 3 and influencing both structural stability and transmission performance.

In addition, by sleeving the bearing 6 on the transmission shaft 3 and/or the output shaft 501 and making the bearing 6 contact with the wall surface of the installation cavity 102, the centering accuracy of the transmission shaft 3 and/or the output shaft 501 during installation can be improved, and in addition, the position of the transmission shaft 3 and/or the output shaft 501 is not deviated during the process that the driving device 5 drives the transmission shaft 3 to rotate, so that the position stability of the transmission shaft 3 and/or the output shaft 501 is improved.

In addition, the spherical rotor pump 100 further includes a support block 9, the support block 9 is disposed on a side of the bearing 6 away from the diaphragm 103, and the support block 9 is fixed in the mounting cavity 102. The support blocks 9 may act to block foreign objects on the side of the bearing 6 remote from the spacer 103, thereby preventing foreign objects from contacting the bearing 6 and adversely affecting the performance of the bearing 6.

In some embodiments, the body portion 502 has an end surface 503 disposed towards the pump housing 1, the end surface 503 being formed with a raised structure 504, the raised structure 504 being located within the mounting cavity 102, the support block 9 being in abutment with the raised structure 504; the radial dimension of the support blocks 9 is greater than the radial dimension of the raised structures 504.

By making the supporting block 9 abut against the protruding structure 504 on the end of the main body 502, the supporting block 9 and the protruding structure 504 together form a blocking structure for blocking external sundries, which not only can block solid sundries, but also has a certain blocking effect on liquid sundries, thereby better protecting the bearing 6. In addition, the radial dimension of the supporting block 9 is larger than the radial dimension of the protruding structure 504, which is beneficial to reduce the contact area between the two, so that the pressure between the two can be increased, and the contact between the two is more compact.

In addition, the supporting block 9 and the bearing 6 may be pressed by the protrusion structure 504 so that the bearing 6 is tightly abutted against the spacer 7, thereby the spacer 7, the bearing 6 and the supporting block 9 are all fastened and mounted along the axial direction of the transmission shaft 3.

In some embodiments, as shown in fig. 3 or fig. 4, the driving rotor 201 includes a first supporting member 204 and a first encapsulant 205, the first supporting member 204 is wrapped inside the first encapsulant 205 to serve as an inner skeleton of the driving rotor 201, and the transmission shaft 3 extends into the first encapsulant 205 and is connected to the first supporting member 204.

In this embodiment, the active rotor 201 includes a first support 204 and a first encapsulant 205 wrapped around the outside of the first support 204, and the first support 204 may be made of a material having a higher strength, such as a metal material. Thereby, the structural strength of the whole active rotor 201 can be improved, and the first colloid 205 can form a gap seal with the inner wall of the pump casing 1 better. On the basis, the transmission shaft 3 extends into the first colloid 205 and is connected with the first bearing 6, so that the connection strength between the transmission shaft 3 and the driving rotor 201 is improved, and the transmission stability can be improved.

It will be appreciated that the drive shaft 3 may also be made of a stronger material, such as a metallic material. In this way, the transmission shaft 3 can have a better structural strength, so that the transmission can be performed more stably.

Further, the transmission shaft 3 may be fixedly connected to the first supporting member 204, that is, the two may be separately formed and connected by means of screw connection, rivet connection, welding, etc. Alternatively, the drive shaft 3 and the first support 204 may be formed as a single piece, i.e. they may be formed by the same manufacturing process (e.g. metal casting).

In some embodiments, the driven rotor 202 includes a second support 206 and a second encapsulant 207, the second encapsulant 207 covering at least a portion of the second support 206. In this embodiment, the driven rotor 202 includes a second support 206 and a second encapsulant 207 covering at least a portion of the second support 206, and the second support 206 may be made of a material having higher strength, such as a metallic material. Thereby, the structural strength of the driven rotor 202 as a whole can be improved, and the second encapsulant 207 can form a gap seal with the inner wall of the pump casing 1 better.

In some embodiments, as shown in fig. 11, the spherical rotor pump 100 further includes a limiting structure 10, where the limiting structure 10 is disposed between the transmission shaft 3 and the pump casing 1, and the limiting structure 10 is used to limit the movement of the transmission shaft 3 relative to the pump casing 1 along the axial direction thereof.

Limited by the precision of the machining, there may be room for movement after the rotor assembly 2 is assembled with the pump housing 1. This makes the rotor assembly 2 susceptible to axial play, resulting in increased friction between the rotor assembly 2 and the pump housing 1.

In this embodiment, a limiting structure 10 is disposed between the transmission shaft 3 and the pump casing 1, and the limiting structure 10 can limit the motion of the transmission shaft 3 along the axial direction of the pump casing 1, and since the transmission shaft 3 is connected with the driving rotor 201 in the rotor assembly 2, the motion of the driving rotor 201 along the axial direction of the transmission shaft 3 can be further limited, so as to reduce the possibility of axial movement of the driving rotor 201, thereby improving the problem that the rotor assembly 2 is easy to generate axial movement.

In some embodiments, as shown in fig. 11, the pump casing 1 is formed with a limit surface 111, and the limit structure 10 includes a first member 1001, a second member 1002, and a spacer 1004. The first member 1001 is connected to the drive shaft 3 such that the first member 1001 is fixed to the drive shaft 3 in the axial direction of the drive shaft 3, the second member 1002 is fixedly connected to the pump casing 1, the spacer 1004 abuts against the stopper surface 111, and the first member 1001 is regulated between the spacer 1004 and the second member 1002.

The first member 1001 is restrained between the spacer 1004 and the second member 1002 such that the movement of the first member 1001 in the axial direction of the propeller shaft 3 is restrained. Further, because the first member 1001 is in driving connection with the drive, the movement of the drive shaft 3 in the direction of its own axis relative to the pump housing 1 is restricted.

In one embodiment, as shown in fig. 11, the first member 1001 is a bearing 6 sleeved on the transmission shaft 3. In this embodiment, the bearing 6 fitted over the transmission shaft 3 is restrained between the spacer 1004 and the second member 1002, thereby restraining the movement of the transmission shaft 3 in the own axis direction. In addition, the bearing 6 can be in contact with the wall surface of the pump casing 1, so that the centering precision of the transmission shaft 3 during installation can be improved through the bearing 6, and in addition, the position of the transmission shaft 3 can be ensured not to deviate in the process that the driving device 5 drives the transmission shaft 3 to rotate, so that the position stability of the transmission shaft 3 is improved.

Further, the bearing 6 includes a bearing outer ring 602 and a bearing inner ring 601 connected to the bearing outer ring 602, wherein the bearing inner ring 601 is fastened to the drive shaft 3 such that the bearing 6 is fixed relative to the drive shaft 3 in the axial direction of the drive shaft 3. One end of the bearing outer race 602 abuts the spacer 1004, and the other end of the bearing outer race 602 abuts the second member 1002, that is, the bearing outer race 602 is restrained between the spacer 1004 and the second member 1002. Thereby, the movement of the drive shaft 3 in the own axis direction with respect to the pump housing 1 is restricted.

Further, as shown in fig. 11, the limiting structure 10 may further include a third member 1003, where the third member 1003 is fixedly connected to the transmission shaft 3, and the third member 1003 abuts against an end of the bearing inner ring 601 away from the spacer 1004. By providing the third member 1003, the axial stability between the drive shaft 3 and the bearing 6 can be further ensured, and the play of the drive shaft 3 relative to the bearing 6 caused by the loose tight fit between the bearing inner race 601 and the drive shaft 3 can be prevented.

Specifically, the third member 1003 may be a clip spring 11 sleeved on the transmission shaft 3, which has the advantage of convenient installation. In other embodiments, the third member 1003 may be a pin fixedly mounted on the transmission shaft 3, and the pin is used as the third member 1003, which has the advantage of stable connection.

In another embodiment, the first member 1001 is a clamp spring 11 sleeved on the transmission shaft 3, or the first member 1001 is a pin fixedly mounted on the transmission shaft 3. In this embodiment, no bearing is provided on the drive shaft 3, and at this time, the clip spring 11 or pin fitted over the drive shaft 3 is restrained between the spacer 1004 and the second member 1002, thereby restraining the movement of the drive shaft 3 in the own axis direction.

In some embodiments, as shown in fig. 11, the second member 1002 is a snap ring 12 fixedly connected to the pump casing 1, and the snap ring 12 is used as the second member 1002, which has advantages of convenient installation, easy material obtaining, lower cost, and the like.

Further, as shown in fig. 11, the pump casing 1 further has a mounting cavity 102, the limit structure 10 is located in the mounting cavity 102, a part of the transmission shaft 3 is located in the accommodating cavity 101, another part of the transmission shaft 3 is located in the mounting cavity 102, and the snap ring 12 is in interference fit with the mounting cavity 102. In this embodiment, the pump housing 1 has a receiving chamber 101 for receiving the rotor assembly 2 and a mounting chamber 102, the mounting chamber 102 being adapted to receive the output shaft 501 of the drive device 5, so that the output shaft 501 of the drive device 5 can be protected by the mounting chamber 102. The limiting structure 10 and a part of the transmission shaft 3 are also located in the installation cavity 102, so that the limiting structure 10 and the transmission shaft 3 can be under the protection of the installation cavity 102, and external sundries cannot touch the output shaft 501, the transmission shaft 3, the limiting structure 10 and the like. On this basis, the snap ring 12 may be interference fit with the mounting cavity 102 to achieve a fixed connection between the second member 1002 (the snap ring 12) and the pump casing 1.

In some embodiments, as shown in fig. 11, 12, 13, and 14, the driving rotor 201 and the driven rotor 202 are connected by a pin 208, so that the driven rotor 202 can rotate about the pin 208 relative to the driving rotor 201. In this embodiment, the driving rotor 201 and the driven rotor 202 are connected by a pin 208, so that the driving rotor 201 and the driven rotor 202 are connected together. The arrangement makes the driving rotor 201 and the driven rotor 202 into a whole structure, so that on the basis that the limit structure 10 limits the motion of the transmission shaft 3 relative to the pump shell 1 along the self axis direction, the possibility of the driving rotor 201 and the driven rotor 202 moving is reduced, and the position stability of the driving rotor 201 and the driven rotor 202 relative to the pump shell 1 is improved.

In some embodiments, as shown in fig. 11, 15, 16 and 17, the active rotor 201 includes a first supporting member 204 and a first encapsulant 205, where a portion of the first supporting member 204 is wrapped inside the first encapsulant 205 to serve as an inner skeleton of the active rotor 201, and another portion of the first supporting member 204 is located outside the first encapsulant 205 to form a connection portion 2041. The driven rotor 202 includes a second support 206 and a second encapsulant 207, the second encapsulant 207 covering at least a portion of the second support 206. The second encapsulant 207 is provided with a through slot 2071, and the connecting portion 2041 extends into the second encapsulant 207 through the through slot 2071 and is connected with the second support 206 through a pin 208.

In this embodiment, the active rotor 201 includes the first support 204 and the first encapsulant 205, and the first support 204 may be made of a material having higher strength, thereby improving the structural strength of the active rotor 201 as a whole. Outside the active rotor 201 is a first encapsulant 205, and the first encapsulant 205 may better form a gap seal with the inner wall of the pump casing 1. Likewise, the driven rotor 202 includes the second support 206 and the second encapsulant 207, and the second support 206 may be made of a material having a high strength, thereby improving the structural strength of the driven rotor 202 as a whole. Outside the driven rotor 202 is a second encapsulant body 207, and the second encapsulant body 207 may better form a gap seal with the inner wall of the pump casing 1.

In addition, a part of the first supporting member 204 is wrapped inside the first encapsulant 205, and another part of the first supporting member is located outside the first encapsulant 205 to form a connecting portion 2041. The second encapsulant 207 is provided with a through slot 2071, and the connecting portion 2041 extends into the second encapsulant 207 through the through slot 2071 and is connected with the second support 206 through a pin 208. The arrangement is such that the first support 204 and the second support 206 are connected by the pin 208, thereby realizing the connection between the driving rotor 201 and the driven rotor 202, so that the driving rotor 201 and the driven rotor 202 are formed into a unitary structure.

Further, as shown in fig. 11, the width of the through groove 2071 is larger than the width of the connection portion 2041 so that a space is provided between the connection portion 2041 and the side wall of the through groove 2071. By this arrangement, the connecting portion 2041 has a certain swinging space, so that interference between the connecting portion 2041 and the second encapsulant 207 can be avoided in the process that the driving rotor 201 drives the driven rotor 202 to rotate.

In some embodiments, as shown in fig. 12, the driving rotor 201 has a first axis a about which the driving rotor 201 can rotate relative to the pump casing 1, the driven rotor 202 has a second axis b about which the driven rotor 202 can rotate relative to the pump casing 1, the first axis a intersecting the second axis b; the pin 208 intersects both the first axis a and the second axis b.

In this embodiment, the first axis a of the driving rotor 201 intersects the second axis b of the driven rotor 202, and the pin 208 intersects both the first axis a and the second axis b. When the driving rotor 201 drives the driven rotor 202 to rotate, the driving rotor 201 continuously rotates around the first axis, the driven rotor 202 continuously rotates around the second axis b, and at the same time, the driven rotor 202 performs reciprocating swinging motion around the pin 208. In this process, the volume of the variable volume chamber 203 defined by the driving rotor 201, the driven rotor 202, and the wall surface of the accommodating chamber 101 can be changed.

In some embodiments, as shown in fig. 12, 14, 15 and 16, a groove 210 is provided on the driven rotor 202, the driving rotor 201 is formed with a pin portion 209, the surface of the pin portion 209 is a cylindrical surface or a semi-cylindrical surface, and the pin portion 209 is confined in the groove 210 and can rotate around a third axis c relative to the groove 210; the central axis of the pin 208 coincides with the third axis c.

By the engagement of the pin shaft portion 209 with the groove 210, a seal can be formed between the driving rotor 201 and the driven rotor 202, so that the variable volume chamber 203 having sealability can be defined between the driving rotor 201, the driven rotating shaft, and the wall surface of the accommodation chamber 101. In addition, the pin shaft portion 209 is limited in the groove 210 and can rotate around the third axis c relative to the groove 210, that is, the third axis c is the rotation center of the pin shaft portion 209, and on the basis, the central axis of the pin shaft 208 coincides with the third axis c, so that the pin shaft portion 209 can be always in a good matching state with the groove 210 in the process of making the driven rotor 202 perform the reciprocating swinging motion around the pin shaft 208, and thus good tightness is maintained between the driving rotor 201 and the driven rotor 202. On the other hand, the central axis of the pin shaft 208 coincides with the third axis c, which is also beneficial to the smooth movement of the rotor assembly 2 and prevents the occurrence of movement jamming.

In some embodiments, the spherical rotor pump 100 further comprises a driving device 5 and a constraint structure 13, wherein the driving device 5 has an output shaft 501, and the output shaft 501 can drive the transmission shaft 3 to rotate. The restraint structure 13 is sleeved on the output shaft 501 and the transmission shaft 3 so as to keep the output shaft 501 and the transmission shaft 3 fixed.

In the spherical rotor pump in the related art, the phenomenon that the rotor assembly rotates unsmoothly easily occurs, and the problem of pump clamping possibly occurs in severe cases. The main reason why the rotation of the rotor assembly of the spherical rotor pump in the related art is not smooth is that the coaxiality between the output shaft of the driving device and the transmission shaft is poor, which causes the rotor assembly to deviate from the expected position, thereby causing the problem that the rotation of the rotor assembly is not smooth, and in severe cases, the problem that the rotor assembly is blocked is caused. In addition, the rotor assembly may also cause increased friction with the pump casing after being out of position from the intended position.

The spherical rotor pump 100 in the present embodiment is provided with a constraint structure 13, and the constraint structure 13 is sleeved on the transmission shaft 3 and the output shaft 501 of the driving device 5, so that the output shaft 501 and the transmission shaft 3 remain fixed. By the retaining action of the restraining structure 13, the coaxiality between the output shaft 501 of the drive device 5 and the propeller shaft 3 can be improved. Thereby, the deviation between the actual position and the expected position of the rotor assembly 2 can be reduced or eliminated, so that the rotor assembly 2 rotates more smoothly, thereby being beneficial to avoiding the problem of pump clamping and the problem of aggravation of friction force between the rotor assembly 2 and the pump shell 1.

Further, as shown in fig. 18, the pump housing 1 further has a mounting cavity 102, and the output shaft 501 and the restraining structure 13 are both located in the mounting cavity 102, and a part of the drive shaft 3 is located in the mounting cavity 102, and another part of the drive shaft 3 extends into the accommodation cavity 101. The restraining structure 13 is a sleeve 14, and a space is provided between the outer wall surface of the sleeve 14 and the wall surface of the mounting cavity 102.

In this embodiment, the pump housing 1 has a receiving chamber 101 for receiving the rotor assembly 2 and a mounting chamber 102, the mounting chamber 102 being adapted to receive the output shaft 501 of the drive device 5, so that the output shaft 501 of the drive device 5 can be protected by the mounting chamber 102. At the same time, the restraint structure 13 and a part of the drive shaft 3 are also located in the installation cavity 102, which makes it possible for the restraint structure 13 and the drive shaft 3 to also be under the protective action of the installation cavity 102. In addition, in this embodiment, the constraint structure 13 is a sleeve 14 that is fitted over the output shaft 501 and the transmission shaft 3, and the axis of the output shaft 501 and the axis of the transmission shaft 3 can be kept collinear by the sleeve 14. Further, the outer wall surface of the sleeve 14 is spaced from the wall surface of the installation cavity 102, so that friction is not generated between the sleeve 14 and the wall surface of the installation cavity 102 when the sleeve rotates with the output shaft 501 and the transmission shaft 3.

Further, as shown in fig. 18, the spherical rotor pump 100 may further include a bearing 6 sleeved on the transmission shaft 3, the bearing 6 being located in the installation cavity 102, an outer wall surface of the bearing 6 being in contact with a wall surface of the installation cavity 102. By arranging the bearing 6 which is sleeved on the transmission shaft 3 and making the bearing 6 contact with the wall surface of the installation cavity 102, the centering precision of the transmission shaft 3 relative to the installation cavity 102 can be improved, so that the position precision of the transmission shaft 3 can be further improved, and in addition, the position of the transmission shaft 3 can be kept from shifting in the process that the driving device 5 drives the transmission shaft 3 to rotate.

Further, as shown in fig. 18, a limiting surface 111 is formed in the mounting cavity 102, the spherical rotor pump 100 further includes a snap ring 12, a gasket 23 and a snap spring 11, the gasket 23 is abutted against the limiting surface 111, the snap ring 12 is in interference fit with the mounting cavity 102, and the snap spring 11 is sleeved on the transmission shaft 3. The bearing 6 comprises a bearing outer ring 602 and a bearing inner ring 601 connected with the bearing outer ring 602, one end of the bearing outer ring 602 is abutted against the gasket 23, the other end of the bearing outer ring 602 is abutted against the clamping ring 12, and the clamping ring 11 is abutted against one end, away from the gasket 23, of the bearing inner ring 601.

The bearing 6 includes a bearing inner ring 601 and a bearing outer ring 602, the bearing inner ring 601 being fastened to the drive shaft 3 such that the bearing 6 is fixed relative to the drive shaft 3 with respect to the axial direction of the drive shaft 3. The bearing outer ring 602 is limited between the gasket 23 and the clamping ring 12, the gasket 23 is abutted against the limiting surface 111 of the mounting cavity 102, and the clamping ring 12 is in interference fit with the mounting cavity 102, so that the motion of the transmission shaft 3 relative to the pump shell 1 along the axial direction can be limited, and the possibility of axial movement of the driving rotor 201 can be reduced due to the fact that the transmission shaft 3 is connected with the driving rotor 201, and the problem of friction force increase between the driving rotor 201 and the pump shell 1 caused by the axial movement of the driving rotor 201 is avoided. In addition, through setting up jump ring 11, can further guarantee the axial stability between transmission shaft 3 and the bearing 6, prevent that the tight fit between bearing inner race 601 and the transmission shaft 3 from taking place not hard up and leading to transmission shaft 3 to float for bearing 6.

In other embodiments, as shown in fig. 19, the pump housing 1 further has a mounting cavity 102, the output shaft 501 and the constraining structure 13 are both located within the mounting cavity 102, a portion of the drive shaft 3 is located within the mounting cavity 102, and another portion of the drive shaft 3 extends into the receiving cavity 101. The restraining structure 13 is a bearing 6, the bearing 6 is positioned in the mounting cavity 102, and the outer wall surface of the bearing 6 is contacted with the wall surface of the mounting cavity 102.

In this embodiment, the constraint structure 13 is a bearing 6 sleeved on the output shaft 501 and the transmission shaft 3, and the bearing 6 is used as the constraint structure 13, so that not only the axis of the output shaft 501 and the axis of the transmission shaft 3 can be kept collinear, but also the outer wall surface of the bearing 6 is in contact with the wall surface of the installation cavity 102, and the centering precision of the transmission shaft 3 relative to the installation cavity 102 can be improved, so that the position precision of the transmission shaft 3 can be further improved. In this embodiment, since the bearing 6 serves both to improve the centering accuracy of the drive shaft 3 and also to serve as the constraint structure 13, this arrangement can reduce the number of parts, thereby contributing to a reduction in the overall size of the spherical rotor pump 100 in the axial direction of the drive shaft 3.

Further, as shown in fig. 19, the driving device 5 further includes a main body 502, and the output shaft 501 is connected to the main body 502. The mounting cavity 102 is formed with a limiting surface 111, the spherical rotor pump 100 further comprises a support block 9, the support block 9 is located in the mounting cavity 102 and abuts against the main body 502, and the bearing 6 is limited between the limiting surface 111 and the support block 9.

In this embodiment, the bearing 6 is tightly fitted over the drive shaft 3, and at the same time, the bearing 6 is restrained between the stopper face 111 of the mounting chamber 102 and the supporting block 9, whereby the movement of the drive shaft 3 in the direction of its own axis relative to the pump housing 1 can be restrained, and since the drive shaft 3 is connected to the drive rotor 201, the possibility of axial play of the drive rotor 201 can be reduced, thereby avoiding the problem of an increase in friction with the pump housing 1 due to the axial play of the drive rotor 201.

In some embodiments, as shown in fig. 20, 21 and 22, the output shaft 501 includes a first mating portion 5011, the first mating portion 5011 is provided with a first contact surface 5012, the drive shaft 3 includes a second mating portion 301, the second mating portion 301 is provided with a second contact surface 3011, and the first contact surface 5012 is tightly abutted against the second contact surface 3011 to enable torque transmission between the output shaft 501 and the drive shaft 3. On the basis that the constraint structure 13 is sleeved on the output shaft 501 and the transmission shaft 3, the first contact surface 5012 of the first matching part 5011 is tightly abutted against the second contact surface 3011 of the second matching part 301, and the arrangement can realize transmission connection between the output shaft 501 and the transmission shaft 3, and in addition, the structure is simple, and the structure is easy to process and realize.

Further, the first contact face 5012 and the second contact face 3011 are both planar. In this way, the first contact surface 5012 and the second contact surface 3011 can be better attached to each other, so that the output shaft 501 and the transmission shaft 3 can be prevented from shaking or vibrating during transmission.

Further, the cross-sectional shape of the first fitting portion 5011 is a first semicircle, the cross-sectional shape of the second fitting portion 301 is a second semicircle, and the radius of the first semicircle is equal to the radius of the second semicircle. Thus, when the first contact surface 5012 of the first fitting portion 5011 and the second contact surface 3011 of the second fitting portion 301 are tightly abutted, the first fitting portion 5011 and the second fitting portion 301 can be joined into a complete cylinder, and the axis of the cylinder coincides with the axis of the output shaft 501 and the axis of the transmission shaft 3.

In other embodiments, the output shaft 501 includes a third mating portion, the drive shaft 3 includes a fourth mating portion, one of the third mating portion and the fourth mating portion is a prismatic structure, the other of the third mating portion and the fourth mating portion is a mounting sleeve, the mounting sleeve has an inner cavity, the shape of the inner cavity matches the prismatic structure, and the prismatic structure fits into the inner cavity. In this embodiment, the output shaft 501 and the transmission shaft 3 are matched with each other by a prism structure and an inner cavity, and the shape of the inner cavity is matched with that of the prism structure, for example, when the prism structure is a quadrangular prism, the cross-sectional shape of the inner cavity is quadrangular, and when the prism structure is a hexagonal prism, the cross-sectional shape of the inner cavity is hexagonal. This arrangement allows torque to be transferred between the output shaft 501 and the drive shaft 3 so that the output shaft 501 can rotate the drive shaft 3. In addition, the output shaft 501 and the transmission shaft 3 can be stressed uniformly in the transmission process.

Further, the prism structure is a regular prism, and the number of sides of the regular prism is greater than or equal to 3 and less than or equal to 6. The prismatic structure is a regular prism, which is beneficial to further improving the stress uniformity of the output shaft 501 and the transmission shaft 3 in the transmission process, thereby being beneficial to prolonging the service lives of the output shaft 501 and the transmission shaft 3. In addition, the number of the side faces of the regular prism is 3 to 6, so that the prism structure is easy to process and manufacture, and the processing precision of the prism structure is improved.

In other embodiments, as shown in fig. 23, 24 and 25, one of the output shaft 501 and the drive shaft 3 is provided with a clamping groove 302, and the other of the output shaft 501 and the drive shaft 3 is provided with a flat shaft portion 5013, the flat shaft portion 5013 being engaged with the clamping groove 302 to enable torque transmission between the output shaft 501 and the drive shaft 3. In this embodiment, torque can be transmitted between the output shaft 501 and the propeller shaft 3 by the engagement of the flat shaft portion 5013 with the card slot 302. In addition, the output shaft 501 and the transmission shaft 3 can be stressed uniformly in the transmission process.

Further, one of the output shaft 501 and the drive shaft 3 is further provided with a mounting hole 303 extending in the axial direction, and the other of the output shaft 501 and the drive shaft 3 is further provided with a mounting portion 5014 connected with the flat shaft portion 5013, the mounting portion 5014 being interference fit with the mounting hole 303. Through the interference fit between the installation department 5014 and the mounting hole 303 for output shaft 501 and transmission shaft 3 remain relatively fixed in the axis direction, like this, also be favorable to avoiding transmission shaft 3 to take place to remove along the axis direction, thereby reduce the possibility that initiative rotor 201 takes place the axial float, and then avoid leading to the problem with the increase of frictional force between pump case 1 because of initiative rotor 201 axial float.

In some embodiments, as shown in fig. 3, 26, the spherical rotor pump 100 further includes a seal 16. Specifically, the pump housing 1 includes a first housing 107 and a second housing 108 connected to the first housing 107, the first housing 107 and the second housing 108 together defining the accommodation chamber 101, the rotor assembly 2 being located within the accommodation chamber 101, and the seal 16 being located between the first housing 107 and the second housing 108 and disposed around the accommodation chamber 101. Wherein, a groove 121 is provided on one of the first housing 107 and the second housing 108, a protrusion 122 is provided on the other of the first housing 107 and the second housing 108, the protrusion 122 extends into the groove 121, and an end face 1221 of the protrusion 122 abuts against the sealing member 16 to press the sealing member 16 in the groove 121.

In the present embodiment, the pump housing 1 includes the first housing 107 and the second housing 108 connected to each other, and the seal 16 provided around the accommodation chamber 101 is provided between the first housing 107 and the second housing 108, whereby a seal can be formed between the first housing 107 and the second housing 108, thereby reducing the risk of leakage of the liquid in the accommodation chamber 101. In addition, a groove 121 and a protrusion 122 are further provided at a contact portion of the first housing 107 and the second housing 108, and the protrusion 122 extends into the groove 121 and presses the sealing member 16 into the groove 121, so that the sealing member 16 can be kept in a pressed state, and thereby, a sealing effect of the sealing member 16 can be improved, thereby further reducing a leakage risk.

In some embodiments, as shown in fig. 26, 27 and 28, the thickness h of the projection 122 gradually decreases in a direction away from the rotor assembly 2.

Taking the case where the groove 121 is provided in the first housing 107 and the protrusion 122 is provided in the second housing 108 as an example, when the first housing 107 is assembled with the second housing 108, the protrusion 122 of the second housing 108 presses the seal 16, and since the thickness h of the protrusion 122 gradually decreases in a direction away from the rotor assembly 2, this causes the protrusion 122 to expand the seal 16 radially outward while pressing the seal 16, thereby subjecting the first housing 107 to a force from the seal 16, under which the first housing 107 undergoes outward micro deformation. In this way, after the first housing 107 and the second housing 108 are assembled, it is beneficial to avoid the increase of friction force caused by the extrusion between the first housing 107 and the rotor assembly 2 when the rotor assembly 2 rotates.

Taking the case where the groove 121 is provided in the second housing 108 and the projection 122 is provided in the first housing 107 as an example, when the first housing 107 is assembled with the second housing 108, the projection 122 in the first housing 107 presses the seal 16, and since the thickness h of the projection 122 gradually decreases in a direction away from the rotor assembly 2, this causes the projection 122 to expand the seal 16 radially outward while pressing the seal 16, thereby subjecting the second housing 108 to a force from the seal 16, under which the second housing 108 undergoes outward micro deformation. In this way, after the first housing 107 and the second housing 108 are assembled, it is beneficial to avoid that the friction force increases when the rotor assembly 2 rotates due to the extrusion between the second housing 108 and the rotor assembly 2.

In some embodiments, as shown in fig. 28 and 29, the protrusion 122 is of annular configuration, such that any location of the seal 16 is subject to the compression of the protrusion 122. In addition, the cross-sectional shape of the protrusion 122 may be configured as a trapezoid, in which a short base of the trapezoid corresponds to a surface of the seal 16 on a side away from the rotor assembly 2, and a long base of the trapezoid corresponds to a surface of the seal 16 on a side close to the rotor assembly 2. Thereby, it is possible to construct a configuration in which the thickness h of the projection 122 gradually decreases in a direction away from the rotor assembly 2.

In some embodiments, as shown at 27, the active rotor 201 has a first axis a about which the active rotor 201 is rotatable relative to the pump housing 1; the driven rotor 202 has a second axis b about which the driven rotor 202 is rotatable relative to the pump housing 1, the first axis a intersecting the second axis b.

In one embodiment, the end face 1221 of the protrusion 122 is perpendicular to the second axis b. At this time, the thickness h of the protrusion 122 is not changed in a direction away from the rotor assembly 2, i.e., the protrusion 122 has a structure in which the thickness h is uniform. In this case, after the first housing 107 and the second housing 108 are assembled, at least it is ensured that the housing in which the groove 121 is located is not slightly deformed outwards or inwards, so that the housing in which the groove 121 is located is prevented from being pressed against the rotor assembly 2 after the assembly is completed.

In another embodiment, as shown in fig. 27, the end face 1221 of the protrusion 122 includes an angle β greater than 90 ° and less than or equal to 135 ° with the second axis b. The end face 1221 of the projection 122 forms an angle β of more than 90 ° with the second axis b, in which case the thickness h of the projection 122 gradually decreases in a direction away from the rotor assembly 2. In this case, when the first housing 107 and the second housing 108 are assembled, the housing in which the groove 121 is located may undergo outward micro deformation. In this way, after the first housing 107 and the second housing 108 are assembled, it is beneficial to avoid that the friction force increases when the rotor assembly 2 rotates due to the extrusion between the housing where the groove 121 is located and the rotor assembly 2.

In some embodiments, as shown in fig. 26, the recess 121 includes a first portion 1211 and a second portion 1212 in communication with each other, the second portion 1212 being located on a side of the first portion 1211 remote from the protrusion 122, wherein the first portion 1211 has a width greater than a width of the second portion 1212, the protrusion 122 being located within the first portion 1211, and the seal 16 being located at least within the second portion 1212. So configured, during assembly of the first housing 107 and the second housing 108, the sealing member 16 enters the second portion 1212 having a smaller width from the first portion 1211 having a larger width under the pressing action of the protrusion 122, and the portion of the sealing member 16 located in the second portion 1212 is always kept in a compressed state, whereby the sealing effect of the sealing member 16 can be further improved, thereby further reducing the risk of leakage.

In some embodiments, as shown in fig. 27 and 30, the first housing 107 and the second housing 108 each include a housing main body portion 131 and a butting portion 132, the housing main body portion 131 having an open end, the butting portion 132 being located outside the housing main body portion 131 and disposed around the open end. The abutting portion 132 of the first housing 107 and the abutting portion 132 of the second housing 108 are connected by a fastener, and the recess 121 and the protrusion 122 are disposed on the abutting portion 132. By providing the abutting portion 132 around the housing main body portion 131 and connecting the abutting portion 132 of the first housing 107 and the second housing 108 by a fastener, the contact area between the first housing 107 and the second housing 108 can be increased, and thus, the sealing performance of the pump housing 1 can be improved, and the connection stability between the first housing 107 and the second housing 108 can be improved.

In some embodiments, as shown in fig. 29, 30, the abutting portion 132 of the first housing 107 and/or the abutting portion 132 of the second housing 108 is provided with a reinforcing rib 133. During operation of the ball rotor pump 100, the first housing 107 and the second housing 108 are subjected to the pressure of the liquid in the variable volume chamber 203, which tends to move the first housing 107 and the second housing 108 away from each other, and the pressure is large, so that the connection portion between the first housing 107 and the second housing 108 is easily deformed. In this embodiment, the abutting portion 132 of the first housing 107 and/or the second housing 108 is provided with the reinforcing rib 133, and by providing the reinforcing rib 133, the structural strength and structural rigidity of the abutting portion 132 can be improved, so that the abutting portion 132 is not easily deformed, thereby facilitating improvement of the connection stability between the first housing 107 and the second housing 108.

In some embodiments, as shown in fig. 27, the distance L1 from the groove 121 to the wall surface of the accommodating cavity 101 is greater than or equal to 0.8mm, which is beneficial to the structure between the groove 121 and the accommodating cavity 101 having better structural strength and structural rigidity, and being not easy to break or deform.

In some embodiments, as shown in fig. 28, the distance L2 from the groove 121 to the outer surface of the abutting portion 132 is greater than or equal to 0.8mm, which is advantageous in that the structure between the groove 121 and the outer surface of the abutting portion 132 has better structural strength and structural rigidity, and is not easily damaged or deformed.

In some embodiments, as shown in fig. 28, a distance L3 from the bottom of the groove 121 to the surface of the abutting portion 132 in the thickness direction is greater than or equal to 0.8mm, which is advantageous in that the structure between the bottom of the groove 121 and the surface of the abutting portion 132 in the thickness direction has good structural strength and structural rigidity, and is not easily broken or deformed.

In some embodiments, as shown in fig. 28, the width w of the protrusion 122 is greater than or equal to 0.8mm, which is advantageous in that the protrusion 122 has a good structural strength and rigidity, and is not easily broken or deformed.

In some embodiments, the distance L2 of the groove 121 to the outer surface of the abutment 132 is greater than the distance L1 of the groove 121 to the wall of the receiving cavity 101. So set up, the setting position of recess 121 is comparatively far away from the surface of butt joint portion 132, and is nearer with holding chamber 101, because sealing member 16 sets up in recess 121, in this way, can avoid more liquid to enter into the clearance between two butt joint portions 132. In addition, in the case where the groove 121 is provided closer to the accommodating chamber 101, it is advantageous to make the moment arm of the moment formed by the pressure of the liquid from the inside of the variable-volume chamber 203 shorter, thereby being more advantageous to improve the connection stability between the first housing 107 and the second housing 108.

In some embodiments, as shown in fig. 29, the seal 16 is an annular seal 16, thereby enabling the seal 16 to be disposed around the receiving cavity 101, thereby forming a closed sealing structure between the first housing 107 and the second housing 108. In addition, the cross-sectional shape of the sealing member 16 is circular, so that the sealing member 16 has more remarkable deformation under the extrusion action of the protrusions 122, and therefore, the space in the groove 121 can be more fully filled and closely contacted with the wall surface of the groove 121, so that better sealing performance is obtained.

In some embodiments, as shown in fig. 12, 31, 32, 33, and 34, the driven rotor 202 has a second axis b about which the driven rotor 202 is rotatable relative to the pump casing 1, the driving rotor 201 has a first axis a about which the driving rotor 201 is rotatable relative to the pump casing 1. The driven rotor 202 includes a base 214 and a pin shaft portion 209 provided on the base 214, and the driving rotor 201 is provided with a groove 210, and the pin shaft portion 209 is restrained in the groove 210 and rotatable about a third axis c with respect to the groove 210. The pin shaft portion 209 has a first mating surface 2091 and side surfaces 2092 located on both sides of the first mating surface 2091, the first mating surface 2091 connects the two side surfaces 2092, the first mating surface 2091 is an arc surface and has a central angle smaller than or equal to 180 °, and a minimum distance between the two side surfaces 2092 is equal to a chord length d of the first mating surface 2091.

In the present embodiment, the pin shaft 209 has a first mating surface 2091 and side surfaces 2092 located on two sides of the first mating surface 2091, wherein the first mating surface 2091 is an arcuate surface, and the first mating surface 2091 is configured to mate with the groove 210, such that the pin shaft 209 is confined within the groove 210 and is capable of rotating about the third axis c relative to the groove 210. Since the first mating surface 2091 is an arcuate surface and has a central angle of 180 ° or less, the first mating surface 2091 does not tend to shrink inwardly at positions near both sides. In addition, the minimum distance between the two side surfaces 2092 on either side of the first mating surface 2091 is equal to the chord d of the first mating surface 2091, which also does not cause the two side surfaces 2092 to tend to contract inwardly. Thus, the reverse buckle is prevented from being formed between the side part of the pin shaft part 209 and the base part 214, so that the possibility that the rotor where the groove 210 is located interferes with the pin shaft part 209 or the base part 214 when the pin shaft part 209 and the groove 210 are matched to rotate can be reduced, and the problem of abrasion caused by interference can be further reduced.

In some embodiments, referring to fig. 34, both side surfaces 2092 are planar, and the two side surfaces 2092 are disposed parallel to each other. In the case where the side 2092 is planar, it is advantageous to make the volume of the formed variable volume chamber 203 larger, so that the single pump volume can be increased. In addition, in the case where the two side surfaces 2092 are parallel to each other, the distance between the two side surfaces 2092 can be set to satisfy the setting requirement by making the distance between the two side surfaces 2092 at any position equal to the chord length of the first mating surface 2091.

In other embodiments, the two sides 2092 may also be curved. At this time, it is necessary to obtain a position where the distance between the two side surfaces 2092 is minimum, and to ensure that the distance between the two side surfaces 2092 at this position is equal to the chord length of the first mating surface 2091.

In other embodiments, both sides 2092 are planar and the spatial plane of one side 2092 is at an angle greater than 0 ° and less than or equal to 15 ° to the spatial plane of the other side 2092. In this embodiment, the included angle between the space plane of one side 2092 and the space plane of the other side 2092 is denoted as α, and when α is greater than 0 °, the two sides 2092 are not parallel to each other, but show a tendency to expand outwardly, so that the reverse buckle formed between the side of the pin shaft 209 and the base 214 can be avoided. However, α is not easily too large, which would otherwise result in a reduction in the volume of the variable volume chamber 203. Therefore, in this embodiment, α is limited to a range of 0 ° to 15 ° to reduce the influence on the volume of the variable volume chamber 203.

In some embodiments, as shown in fig. 31 and 35, the groove 210 has a second mating surface 2101 and a clearance portion 2102 located on two sides of the second mating surface 2101, the second mating surface 2101 is an arc surface, the second mating surface 2101 is used to mate with the first mating surface 2091, and a gap is provided between the clearance portion 2102 and the pin shaft 209. In this embodiment, the recess 210 has a second mating surface 2101, and the second mating surface 2101 is arcuate so as to better fit the first mating surface 2091 of the pin portion 209. In addition, the groove 210 further has clearance portions 2102 located at two sides of the second mating surface 2101, a gap is formed between the clearance portions 2102 and the pin shaft portion 209, and the clearance portions 2102 are used for avoiding positions in the process of mating rotation of the pin shaft and the groove 210, so that abrasion caused by interference between the edge position of the groove 210 and the pin shaft portion 209 is prevented.

Further, the gap between the space portion 2102 and the pin portion 209 gradually decreases in a direction approaching the second mating surface 2101. This arrangement is advantageous in that the surface of the groove 210 is smoother and does not have abrupt changes at the position of the space-avoiding portion 2102.

Further, a gap between the clearance portion 2102 and the pin portion 209 is greater than or equal to 0.05mm and less than or equal to 0.6mm. If the gap size between the clearance portion 2102 and the pin shaft portion 209 is too small, the effect of the clearance portion 2102 to prevent abrasion becomes insignificant; on the contrary, if the gap between the clearance portion 2102 and the pin shaft portion 209 is oversized, particulate impurities easily enter between the groove 210 and the pin shaft portion 209, and abrasion between the driven rotor 202 and the driving rotor 201 is increased, and even problems such as jamming and damage occur. In this embodiment, the clearance between the clearance portion 2102 and the pin shaft portion 209 is set to be in the range of 0.05mm to 0.6mm, so that the clearance portion 2102 can exert the abrasion preventing effect well, and the situation that particulate impurities easily enter between the groove 210 and the pin shaft portion 209 can be avoided well.

In some embodiments, as shown in fig. 33 and 35, the base 214 has two first planar portions 2141 facing the driving rotor 201, the two first planar portions 2141 being located on both sides of the pin shaft portion 209, and the driving rotor 201 has two second planar portions 2021 facing the base 214, the two second planar portions 2021 being disposed in one-to-one opposition to the two first planar portions 2141. The pin shaft portion 209, the wall surface of the receiving cavity 101, the first planar portion 2141, and the corresponding second planar portion 2021 together define a volume-changing cavity 203, and the volume of the volume-changing cavity 203 changes during rotation of the pin shaft portion 209 relative to the recess 210 about the third axis.

In this embodiment, the surface of the base 214 facing the driving rotor 201 is formed with two first planar portions 2141, and the surface of the driving rotor 201 facing the driven rotor 202 is formed with two second planar portions 2021, on the basis of which the pin shaft portion 209, the wall surface of the accommodation chamber 101, the first planar portions 2141, and the second planar portions 2021 together define the volume-variable chamber 203. Compared with a curved surface, the plane part is easier to process, and higher processing precision can be obtained, so that the volume of the variable-volume cavity 203 is controlled.

In some embodiments, as shown in fig. 31, an end of the space portion 2102 away from the second mating surface 2101 is a first end 2103, an end of the space portion 2102 close to the second mating surface is a second end 2104, a connection line between the first end 2103 and the third axis is a first connection line, a connection line between the second end 2104 and the third axis is a second connection line, and a first included angle γ is formed between the first connection line and the second connection line; one end of the side surface 2092 away from the first mating surface 2091 is a third end 2093, one end of the side surface 2092 close to the first mating surface 2091 is a fourth end 2094, a connection line between the third end 2093 and the third axis is a third connection line, a connection line between the fourth end 2094 and the third axis is a fourth connection line, and a second included angle θ is formed between the third connection line and the fourth connection line, wherein the first included angle γ is greater than the second included angle θ.

By the arrangement, the extension length of the clearance portion 2102 along the circumferential direction is larger than the extension length of the side surface 2092 along the circumferential direction, so that the clearance portion 2102 can always effectively play a role in avoiding position in the process of matching rotation of the pin shaft portion 209 and the groove 210, and interference and abrasion between the edge position of the groove 210 and the pin shaft portion 209 are prevented.

Further, the second included angle is less than 40 °. If the second included angle is too large, the first included angle is correspondingly too large, which results in the space-avoiding portion 2102 having too large a footprint in the groove 210, and the second mating surface 2101 having too small a footprint in the groove 210, thereby affecting the mating stability of the pin shaft portion 209 and the groove 210, and making the rotor assembly 2 prone to vibration and noise during rotation.

In some embodiments, the ball rotor pump 100 has a first state in which the volume of one of the two variable-volume chambers 203 reaches a minimum and the volume of the other of the two variable-volume chambers 203 reaches a maximum. In the first state, the first planar portion 2141 and the corresponding second planar portion 2021 in any one of the variable volume chambers 203 are maintained at a distance. The minimum volume of the variable volume chamber 203 is greater than 0, that is, the volume of the variable volume chamber 203 is always greater than 0 in the process of rotating the rotor assembly 2, that is, the first plane portion 2141 and the second plane portion 2021 are not contacted with each other, so that the situation that the first plane portion 2141 and the second plane portion 2021 are adhered can be avoided, and the spherical rotor pump 100 cannot work normally due to the adhesion of the first plane portion 2141 and the second plane portion 2021 is prevented.

In some embodiments, as shown in fig. 35, a transition chamfer 2105 is formed between the clearance portion 2102 and the second planar portion 2021. This arrangement provides a more gradual transition between the edges of the recess 210 and the second planar portion 2021, thereby reducing the likelihood of interference and wear of the connection between the recess 210 and the second planar portion 2021 with the pin portion 209.

In some embodiments, the first mating surface 2091 and the second mating surface 2101 are made of materials having the same coefficient of expansion. During rotation of the rotor assembly 2, heat is generated between the first mating surface 2091 of the pin shaft 209 and the second mating surface 2101 of the groove 210 due to friction, and the structure of the driven rotor 202 at the first mating surface 2091 and the structure of the driving rotor 201 at the second mating surface 2101 expand due to thermal expansion and contraction. The first mating surface 2091 and the second mating surface 2101 are made of materials with the same expansion coefficient, so that the expansion degrees of the first mating surface 2091 and the second mating surface 2101 are kept consistent, and the first mating surface 2091 and the second mating surface 2101 can always keep good mating relationship, and the phenomenon of motion clamping stagnation caused by poor mating is prevented.

Further, the first mating surface 2091 and the second mating surface 2101 are made of the same material. In this way, the first mating surface 2091 and the second mating surface 2101 are manufactured to have the same expansion coefficient, so as to ensure that the first mating surface 2091 and the second mating surface 2101 can always maintain a good mating relationship during the rotation of the rotor assembly 2.

In some embodiments, as shown in fig. 33, the base 214 also has an outer surface 2142 for mating with a wall of the receiving cavity 101, the outer surface 2142 being spherical. This facilitates smooth rotation of the driven rotor 202 when it rotates relative to the pump casing 1. In addition, the end surfaces 2095 at the two ends of the pin shaft 209 along the third axis direction are spherical surfaces consistent with the outer surface 2142, so that good tightness between the end surfaces 2095 at the two ends of the pin shaft 209 and the pump casing 1 can be ensured, and further, the sealing performance of the variable volume cavity 203 can be ensured.

Embodiments of the second aspect of the present application provide a tooth-cleaning device 1000, the tooth-cleaning device 1000 including the ball-shaped rotor pump 100 of any of the embodiments described above. As shown in fig. 36, the tooth-cleaning device 1000 may include a body 200, a nozzle 300 provided on the body 200, a ball-shaped rotor pump 100 for delivering a liquid to the nozzle 300, and the like.

In the tooth cleaning device 1000 in the embodiment of the present application, the housing of the spherical rotor pump 100 has a housing cavity 101 and a mounting cavity 102, the housing cavity 101 and the mounting cavity 102 are separated by a partition 103, the rotor assembly 2 is located in the housing cavity 101, and the transmission shaft 3 is arranged through a through hole 104 on the partition 103 in a penetrating manner so as to be connected with the driving rotor 201 in the housing cavity 101. The spherical rotor pump 100 is further provided with a seal ring 4, the seal ring 4 being used to seal a gap between the drive shaft 3 and the wall of the through hole 104 or to seal a gap between the drive shaft 3 and the inner wall of the installation cavity 102. In this way, the risk of liquid spilling from the region of the drive shaft 3 is reduced even if there is a problem of failure of the gap seal between the rotor assembly 2 and the inner wall of the receiving chamber 101.

The foregoing is merely specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think about changes or substitutions within the technical scope of the present application, and the changes and substitutions are intended to be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

Claims

1. A spherical rotor pump, comprising:

the pump comprises a pump shell, a pump body and a control device, wherein the pump shell is provided with a containing cavity and a mounting cavity, the containing cavity and the mounting cavity are separated by a partition board, and the partition board is provided with a through hole;

the rotor assembly comprises a driving rotor and a driven rotor, the driving rotor and the driven rotor are both positioned in the accommodating cavity, the wall surfaces of the driving rotor, the driven rotor and the accommodating cavity jointly define a variable-volume cavity, the driving rotor can drive the driven rotor to rotate, and when the driving rotor drives the driven rotor to rotate, the volume of the variable-volume cavity changes;

the transmission shaft penetrates through the through hole, one part of the transmission shaft is positioned in the mounting cavity, and the other part of the transmission shaft extends into the accommodating cavity and is connected with the driving rotor; and

The sealing ring is used for sealing a gap between the transmission shaft and the hole wall of the through hole or sealing a gap between the transmission shaft and the inner wall of the mounting cavity.

2. The spherical rotor pump of claim 1 wherein the seal ring is disposed within the mounting cavity, the seal ring being sleeved on the drive shaft and against the diaphragm.

3. The spherical rotor pump of claim 2, wherein the spherical rotor pump further comprises:

the bearing is positioned in the mounting cavity, the bearing is sleeved on the transmission shaft, the bearing is arranged on one side of the sealing ring away from the partition plate, and the bearing is in contact with the wall surface of the mounting cavity; and

and the isolating piece is positioned between the bearing and the sealing ring.

4. A spherical rotor pump as claimed in claim 3, wherein the mounting cavity comprises a first section and a second section in communication with each other, the second section being located on a side of the first section remote from the diaphragm;

the cross-sectional area of the second section is larger than that of the first section, so that a step-shaped limiting surface is formed at the connecting position of the second section and the first section, the sealing ring is positioned on the first section, the bearing and the separator are both positioned on the second section, and the separator is propped against the limiting surface.

5. The spherical rotor pump of claim 4 wherein the spacer is in close abutment with the seal ring such that the seal ring is compressed in the axial direction of the drive shaft;

wherein, before the sealing ring is not compressed, the dimension of the sealing ring along the axial direction of the transmission shaft is larger than the dimension of the first section along the axial direction of the transmission shaft.

6. A spherical rotor pump as claimed in claim 3, wherein the bearing comprises a bearing inner race and a bearing outer race connected to the bearing inner race, the bearing inner race being fixedly secured to the drive shaft;

the spacer is an annular spacer having an inner diameter greater than an outer diameter of the bearing inner race such that the spacer and the bearing inner race are radially spaced apart.

7. A spherical rotor pump as claimed in claim 3, wherein the bearing comprises a bearing inner race and a bearing outer race connected to the bearing inner race, the bearing inner race being fixedly secured to the drive shaft;

the spacer is an annular spacer, the inner diameter of the spacer is smaller than the outer diameter of the bearing inner ring, an avoidance gap is formed on one side, close to the bearing, of the spacer, and the avoidance gap is arranged opposite to the bearing inner ring so as to avoid the bearing inner ring.

8. The spherical rotor pump of claim 1 wherein the seal ring is disposed within the receiving cavity, the seal ring being sleeved on the drive shaft and against the diaphragm.

9. The ball rotor pump according to claim 8, wherein a first seating groove is provided in the receiving chamber, the seal ring being located in the first seating groove.

10. The ball rotor pump of claim 9, further comprising an anti-wear gasket disposed between the active rotor and the seal ring.

11. The spherical rotor pump of claim 10 wherein a second seating groove is further disposed in the receiving chamber, the second seating groove in communication with the first seating groove, a portion of the wear pad structure being located in the second seating groove, the first seating groove having a radial dimension that is less than a radial dimension of the second seating groove.

12. The ball rotor pump of claim 11, wherein the thickness of the wear pad is greater than the depth of the second seating groove such that a portion of the wear pad structure protrudes beyond the second seating groove.

13. The spherical rotor pump of claim 11 wherein the rotor assembly includes a driving rotor and a driven rotor, both located within the receiving cavity, the drive shaft being connected to the driving rotor;

the anti-abrasion wear-resistant device is characterized in that a limiting end face is arranged at one end, close to the anti-abrasion gasket, of the driving rotor, the limiting end face is a plane, and the limiting end face abuts against the anti-abrasion gasket.

14. The spherical rotor pump as recited in claim 13 wherein a limit portion is formed at an end of the driving rotor remote from the driven rotor, the limit end surface being formed at the limit portion;

the accommodating cavity is internally provided with a third accommodating groove, the third accommodating groove is communicated with the second accommodating groove, the limiting part is positioned in the third accommodating groove, and the radial size of the second accommodating groove is smaller than that of the third accommodating groove.

15. The spherical rotor pump of claim 11 wherein the wear pad is in close abutment with the seal ring such that the seal ring is compressed in the axial direction of the drive shaft;

before the sealing ring is not compressed, the dimension of the sealing ring along the axial direction of the transmission shaft is larger than the dimension of the first placement groove along the axial direction of the transmission shaft.

16. The spherical rotor pump of claim 1 wherein the seal ring is a Y-shaped seal ring comprising a seal ring body having an inner lip and an outer lip disposed on one side thereof, the inner lip and the outer lip abutting the diaphragm.

17. The spherical rotor pump of claim 1 wherein the pump housing comprises a first housing and a second housing, the first housing and the second housing being connected, the first housing and the second housing together defining the receiving cavity, the second housing defining the mounting cavity;

the spherical rotor pump further comprises a driving device, the driving device comprises a main body part and an output shaft connected with the main body part, the main body part is connected with the second shell, and the output shaft is positioned in the mounting cavity and connected with the transmission shaft;

the spherical rotor pump further comprises a bearing, the bearing is positioned in the mounting cavity, the bearing is sleeved on the transmission shaft and/or the output shaft, the bearing is arranged on one side, far away from the partition plate, of the sealing ring, and the bearing is in contact with the wall surface of the mounting cavity;

The spherical rotor pump further comprises a supporting block, the supporting block is arranged on one side, away from the partition plate, of the bearing, and the supporting block is fixed in the installation cavity.

18. The spherical rotor pump as recited in claim 17 wherein the body portion has an end face disposed toward the pump housing, the end face being formed with a boss structure, the boss structure being located within the mounting cavity, the support block being in abutment with the boss structure; the radial dimension of the supporting block is larger than the radial dimension of the protruding structure.

19. The spherical rotor pump of claim 1, wherein the driving rotor comprises a first support member and a first packing body, the first support member is wrapped inside the first packing body to serve as an inner skeleton of the driving rotor, and the transmission shaft extends into the first packing body and is connected with the first support member, wherein the transmission shaft is fixedly connected with the first support member, or the transmission shaft and the first support member are in an integrated structure;

and/or the driven rotor comprises a second support and a second encapsulant covering at least part of the second support.

20. The spherical rotor pump of claim 1 further comprising a limit structure disposed between the drive shaft and the pump housing, the limit structure configured to limit movement of the drive shaft relative to the pump housing in a direction of its own axis.

21. The spherical rotor pump of claim 20 wherein the pump housing is formed with a stop surface;

the limiting structure comprises a first member, a second member and a gasket, wherein the first member is connected with the transmission shaft, so that the first member is fixed relative to the transmission shaft along the axial direction of the transmission shaft, the second member is fixedly connected with the pump shell, the gasket is abutted to the limiting surface, and the first member is limited between the gasket and the second member.

22. The spherical rotor pump of claim 21 wherein the first member is a bearing sleeved on the drive shaft;

the bearing comprises a bearing outer ring and a bearing inner ring connected with the bearing outer ring, the bearing inner ring is fastened on the transmission shaft, one end of the bearing outer ring is abutted against the gasket, and the other end of the bearing outer ring is abutted against the second component.

23. The spherical rotor pump of claim 22, wherein the spacing structure further comprises a third member fixedly connected to the drive shaft, the third member abutting an end of the bearing inner race remote from the spacer.

24. The spherical rotor pump of claim 23 wherein the third member is a snap spring that is sleeved on the drive shaft or a pin that is fixedly mounted to the drive shaft.

25. The ball rotor pump according to claim 21, wherein the first member is a snap spring that is sleeved on the drive shaft, or the first member is a pin that is fixedly mounted on the drive shaft.

26. The spherical rotor pump of claim 21 wherein the second member is a snap ring, the snap ring being an interference fit with the mounting cavity.

27. The ball rotor pump as claimed in claim 20, wherein the driving rotor and the driven rotor are connected by a pin.

28. The spherical rotor pump of claim 27 wherein the active rotor includes a first support and a first encapsulant, a portion of the first support being encased within the first encapsulant to act as an inner skeleton of the active rotor, another portion of the first support being positioned outside of the first encapsulant to form a connection;

The driven rotor comprises a second supporting piece and a second wrapping body, the second wrapping body covers at least part of the second supporting piece, a through groove is formed in the second wrapping body, and the connecting portion extends into the second wrapping body through the through groove and is connected with the second supporting piece through the pin shaft.

29. The ball rotor pump according to claim 28, wherein the width of the through groove is greater than the width of the connection portion such that there is a space between the connection portion and the side wall of the through groove.

30. The spherical rotor pump of claim 27 wherein the driving rotor has a first axis about which the driving rotor is rotatable relative to the pump housing, the driven rotor has a second axis about which the driven rotor is rotatable relative to the pump housing, the first axis intersecting the second axis;

the driven rotor is provided with a groove, the driving rotor is provided with a pin shaft part, the surface of the pin shaft part is a cylindrical surface or a semi-cylindrical surface, and the pin shaft part is limited in the groove and can rotate around a third axis relative to the groove; the central axis of the pin shaft coincides with the third axis.

31. The spherical rotor pump of claim 1 further comprising a drive device and a constraining structure, the drive device having an output shaft capable of rotating the drive shaft;

the restraining structure is sleeved on the output shaft and the transmission shaft so that the output shaft and the transmission shaft are kept fixed.

32. The ball rotor pump as claimed in claim 31, wherein the output shaft and the constraining structure are both located within the mounting cavity, a portion of the drive shaft being located within the mounting cavity, another portion of the drive shaft extending into the receiving cavity;

the restraining structure is a sleeve, and a space is reserved between the outer wall surface of the sleeve and the wall surface of the mounting cavity.

33. The ball rotor pump as claimed in claim 31, wherein the output shaft and the constraining structure are both located within a mounting cavity, a portion of the drive shaft being located within the mounting cavity, another portion of the drive shaft extending into the receiving cavity;

the restraining structure is a bearing, the bearing is positioned in the mounting cavity, and the outer wall surface of the bearing is contacted with the wall surface of the mounting cavity.

34. The ball rotor pump according to claim 33, wherein the drive device further comprises a main body portion, the output shaft being connected to the main body portion;

the mounting cavity is internally provided with a limiting surface, the spherical rotor pump further comprises a supporting block, the supporting block is positioned in the mounting cavity and is abutted to the main body part, and the bearing is limited between the limiting surface and the supporting block.

35. The ball rotor pump according to claim 31, wherein the output shaft comprises a first mating portion provided with a first contact surface, and the drive shaft comprises a second mating portion provided with a second contact surface, the first contact surface being in tight abutment with the second contact surface to enable torque transfer between the output shaft and the drive shaft.

36. The ball rotor pump as claimed in claim 35, wherein the first contact surface and the second contact surface are each planar.

37. The spherical rotor pump of claim 35, wherein the first mating portion has a cross-sectional shape that is a first semicircle and the second mating portion has a cross-sectional shape that is a second semicircle, the radius of the first semicircle being equal to the radius of the second semicircle.

38. The spherical rotor pump of claim 31 wherein the output shaft includes a third mating portion and the drive shaft includes a fourth mating portion, one of the third and fourth mating portions being a prismatic structure and the other of the third and fourth mating portions being a mounting sleeve, the mounting sleeve having an interior cavity shaped to mate with the prismatic structure, the prismatic structure mating with the interior cavity.

39. The spherical rotor pump as recited in claim 31, wherein one of the output shaft and the drive shaft is provided with a detent, and the other of the output shaft and the drive shaft is provided with a flat shaft portion that mates with the detent to enable torque transfer between the output shaft and the drive shaft.

40. The spherical rotor pump as recited in claim 39 wherein one of the output shaft and the drive shaft is further provided with an axially extending mounting hole, the other of the output shaft and the drive shaft being further provided with a mounting portion connected to the flat shaft portion, the mounting portion being an interference fit with the mounting hole.

41. The ball rotor pump of claim 1, further comprising a seal;

the pump shell comprises a first shell and a second shell connected with the first shell, the first shell and the second shell jointly define the containing cavity, and the sealing piece is positioned between the first shell and the second shell and surrounds the containing cavity;

one of the first shell and the second shell is provided with a groove, the other one of the first shell and the second shell is provided with a protrusion, the protrusion stretches into the groove, and the end face of the protrusion abuts against the sealing element so as to press the sealing element into the groove.

42. The spherical rotor pump of claim 41, wherein the thickness of the lobes tapers in a direction away from the rotor assembly.

43. The spherical rotor pump as recited in claim 42 wherein the lobes are of annular configuration and the cross-sectional shape of the lobes is trapezoidal.

44. The spherical rotor pump of claim 41 wherein the drive rotor has a first axis about which the drive rotor is rotatable relative to the pump housing;

The driven rotor having a second axis about which the driven rotor is rotatable relative to the pump housing, the first axis intersecting the second axis;

the end face of the protrusion is perpendicular to the second axis, or an included angle between the end face of the protrusion and the second axis is greater than 90 ° and less than or equal to 135 °.

45. The ball rotor pump according to claim 41, wherein the groove comprises a first portion and a second portion in communication with each other, the second portion being located on a side of the first portion remote from the projection, the first portion having a width greater than a width of the second portion, the projection being located within the first portion, the seal being located at least within the second portion.

46. The spherical rotor pump of claim 41 wherein the first and second housings each include a housing body portion having an open end and a mating portion located outside of the housing body portion and disposed about the open end.

47. The ball rotor pump as claimed in claim 46, wherein the abutment of the first housing and/or the abutment of the second housing is provided with stiffening ribs.

48. The spherical rotor pump of claim 46 wherein the groove is a distance greater than or equal to 0.8mm from the wall of the containment chamber;

and/or the width of the protrusion is greater than or equal to 0.8mm.

49. The ball rotor pump as claimed in claim 46, wherein the distance of the groove from the outer surface of the abutment is greater than the distance of the groove from the wall of the receiving chamber.

50. The spherical rotor pump of claim 41 wherein the seal member is an annular seal member, the seal member having a circular cross-sectional shape.

51. The spherical rotor pump of claim 1 wherein the driven rotor has a second axis about which the driven rotor is rotatable relative to the pump housing;

the driving rotor is provided with a first axis, the driving rotor can rotate around the first axis relative to the pump shell, the driven rotor comprises a base part and a pin shaft part arranged on the base part, the driving rotor is provided with a groove, and the pin shaft part is limited in the groove and can rotate around a third axis relative to the groove;

The pin shaft part is provided with a first matching surface and side surfaces positioned at two sides of the first matching surface, the first matching surface is connected with the two side surfaces, the first matching surface is an arc-shaped surface, the central angle of the first matching surface is smaller than or equal to 180 degrees, and the minimum distance between the two side surfaces is equal to the chord length of the first matching surface.

52. The spherical rotor pump as recited in claim 51 wherein both of said sides are planar and both of said sides are disposed parallel to each other; alternatively, both of the side surfaces are curved surfaces.

53. The spherical rotor pump as recited in claim 51 wherein both of said sides are planar, wherein one of said sides is disposed at a spatial plane that is greater than 0 ° and less than or equal to 15 ° from the spatial plane of the other of said sides.

54. The spherical rotor pump as recited in claim 51 wherein the recess has a second mating surface and a clearance portion on either side of the second mating surface, the second mating surface being arcuate, the second mating surface being configured to mate with the first mating surface, the clearance portion being spaced from the pin portion.

55. The ball rotor pump according to claim 54, wherein a gap between the clearance portion and the pin portion gradually decreases in a direction approaching the second mating surface.

56. The spherical rotor pump of claim 55, wherein a gap between the clearance portion and the pin portion is greater than or equal to 0.05mm and less than or equal to 0.6mm.

57. The spherical rotor pump as recited in claim 54 wherein said base has two first planar portions facing said second rotor, said two first planar portions being located on opposite sides of said pin shaft portion, said second rotor having two second planar portions facing said base, said two second planar portions being disposed in one-to-one opposition to said two first planar portions;

the pin shaft portion, the wall surface of the accommodating cavity, the first plane portion and the corresponding second plane portion jointly define a volume-variable cavity, and the volume of the volume-variable cavity changes in the process that the pin shaft portion rotates around a third axis relative to the groove.

58. The rotary pump according to claim 57, wherein an end of the clearance portion away from the second mating surface is a first end, an end of the clearance portion near the second mating surface is a second end, a line connecting the first end and the third axis is a first line, a line connecting the second end and the third axis is a second line, and a first angle is formed between the first line and the second line;

One end of the side surface, which is far away from the first matching surface, is a third end, one end of the side surface, which is close to the first matching surface, is a fourth end, a connecting line of the third end and the third axis is a third connecting line, a connecting line of the fourth end and the third axis is a fourth connecting line, and a second included angle is formed between the third connecting line and the fourth connecting line;

the first included angle is larger than the second included angle.

59. The ball rotor pump according to claim 58, wherein said second included angle is less than 40 °.

60. The rotary spherical pump of claim 57 wherein the rotary spherical pump has a first state in which the volume of one of the two variable-volume chambers reaches a minimum and the volume of the other of the two variable-volume chambers reaches a maximum;

in the first state, the first plane part and the corresponding second plane part in any one of the variable volume cavities are kept at a distance.

61. The ball rotor pump as claimed in claim 57, wherein a transition chamfer is formed between the clearance portion and the second planar portion.

62. The ball rotor pump as claimed in claim 54, wherein said first mating surface and said second mating surface are fabricated from materials having the same coefficient of expansion.

63. The ball rotor pump as recited in claim 62, wherein said first mating surface and said second mating surface are fabricated from the same material.

64. The spherical rotor pump as recited in claim 51 wherein the base further has an outer surface for mating with a wall of the receiving cavity, the outer surface being spherical;

the end surfaces of the two ends of the pin shaft part along the third axis direction are spherical surfaces consistent with the outer surfaces.

65. A tooth cleaning device comprising the ball rotor pump of any one of claims 1 to 64.