Spherical rotor pump and tooth cleaning device

Abstract

The present application provides a spherical rotor pump and a tooth cleaning device. The spherical rotor pump includes: a pump housing, the pump housing has a receiving chamber and a mounting chamber, the receiving chamber and the mounting chamber are separated by a partition, and the partition is provided with a through hole; a rotor assembly, the rotor assembly includes an active rotor and a driven rotor, the active rotor and the driven rotor are both located in the receiving chamber, the active rotor, the driven rotor and the wall of the receiving chamber jointly define a variable volume chamber, the active rotor can drive the driven rotor to rotate, and when the active rotor drives the driven rotor to rotate, the volume of the variable volume chamber changes; a transmission shaft, the transmission shaft is passed through the through hole, a part of the transmission shaft is located in the mounting chamber, and another part of the transmission shaft extends into the receiving chamber and is connected to the active rotor; and a sealing ring, the sealing ring is used to seal the gap between the transmission shaft and the hole wall of the through hole, or to seal the gap between the transmission shaft and the inner wall of the mounting chamber. In this way, the risk of liquid overflowing from the transmission shaft can be reduced.

Description

Technical Field

[0001] The present application relates to the technical field of oral cleaning, and in particular to a spherical rotor pump and a teeth cleaning device. Background Art

[0002] A spherical rotor pump is a positive displacement liquid delivery device. It usually includes a pump housing and a rotor assembly disposed in the pump housing. The function of pumping water can be achieved through the rotation of the rotor assembly. When the spherical rotor pump is working, the rotor assembly in the pump housing rotates at high speed. The precise fit between the rotor assembly and the pump housing is a necessary condition for sealing the gap inside the pump. Therefore, the parts of the spherical rotor pump are usually processed by precision manufacturing.

[0003] However, the precision manufacturing processing method also brings problems such as complex processes, long manufacturing cycles, and high costs. Some manufacturers have changed some parts to mold batch manufacturing, thereby simplifying the process, improving production efficiency, and reducing costs. However, due to the reduced precision of the parts, the gap seal failure in the pump is prone to occur. When the gap seal fails, the liquid in the pump is likely to overflow from the transmission shaft during the movement of the rotor assembly relative to the pump housing, resulting in leakage. Summary of the invention

[0004] The present application provides a spherical rotor pump and a tooth cleaning device, aiming to reduce the risk of liquid in the pump overflowing from the transmission shaft. The specific technical solution is as follows:

[0005] In a first aspect, the present application provides a spherical rotor pump, which includes: a pump housing, the pump housing having a accommodating chamber and a mounting chamber, the accommodating chamber and the mounting chamber being separated by a partition, the partition being provided with a through hole; a rotor assembly, the rotor assembly including an active rotor and a driven rotor, the active rotor and the driven rotor being both located in the accommodating chamber, the active rotor, the driven rotor and the wall surface of the accommodating chamber jointly defining a variable capacity chamber, the active rotor being able to drive the driven rotor to rotate, and when the active rotor drives the driven rotor to rotate, the volume of the variable capacity chamber changes; a transmission shaft, the transmission shaft being passed through the through hole, a portion of the transmission shaft being located in the mounting chamber, and another portion of the transmission shaft extending into the accommodating chamber and connected to the active rotor; and a sealing ring, the sealing ring being used to seal a gap between the transmission shaft and the hole wall of the through hole, or to seal a gap between the transmission shaft and the inner wall of the mounting chamber.

[0006] The spherical rotor pump in the embodiment of the present application has a housing having a receiving chamber and a mounting chamber, the receiving chamber and the mounting chamber are separated by a partition, the rotor assembly is located in the receiving chamber, and the transmission shaft passes through a through hole on the partition to connect with the active rotor in the receiving chamber. The spherical rotor pump is also provided with a sealing ring, which is used to seal the gap between the transmission shaft and the hole wall of the through hole, or to seal the gap between the transmission shaft and the inner wall of the mounting chamber. In this way, even if there is a problem of gap sealing failure between the rotor assembly and the inner wall of the receiving chamber, the risk of liquid overflowing from the transmission shaft can be reduced.

[0007] In some embodiments, the sealing ring is disposed in the installation cavity, and the sealing ring is sleeved on the transmission shaft and abuts against the partition.

[0008] In some embodiments, the spherical rotor pump further includes: a bearing, the bearing being located in the mounting cavity, the bearing being sleeved on the transmission shaft, the bearing being arranged on a side of the sealing ring away from the partition, the bearing being in contact with a wall surface of the mounting cavity; and an isolating member, the isolating member being located between the bearing and the sealing ring.

[0009] In some embodiments, the mounting cavity includes a first section and a second section that are connected to each other, and the second section is located on a side of the first section away from the partition; the cross-sectional area of ​​the second section is larger than the cross-sectional area of ​​the first section, so that a step-shaped limiting surface is formed at the connection position between the second section and the first section, the sealing ring is located in the first section, the bearing and the isolation member are both located in the second section, and the isolation member is against the limiting surface.

[0010] In some embodiments, the isolation member is tightly 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 compressed, the size of the sealing ring along the axial direction of the transmission shaft is larger than the size of the first section along the axial direction of the transmission shaft.

[0011] In some embodiments, the bearing includes a bearing inner ring and a bearing outer ring connected to the bearing inner ring, and the bearing inner ring is tightly sleeved on the transmission shaft; the isolation member is an annular gasket, and the inner diameter of the gasket is larger than the outer diameter of the bearing inner ring, so that the gasket and the bearing inner ring are radially spaced apart.

[0012] In some embodiments, the bearing includes a bearing inner ring and a bearing outer ring connected to the bearing inner ring, and the bearing inner ring is tightly sleeved on the transmission shaft; the isolation member is an annular gasket, the inner diameter of the gasket is smaller than the outer diameter of the bearing inner ring, and an avoidance gap is formed on the side of the gasket close to the bearing, and the avoidance gap is arranged opposite to the bearing inner ring to avoid the bearing inner ring.

[0013] 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.

[0014] In some embodiments, a first placement groove is provided in the accommodating cavity, and the sealing ring is located in the first placement groove.

[0015] In some embodiments, the spherical rotor pump further includes an anti-wear gasket, which is disposed between the active rotor and the sealing ring.

[0016] In some embodiments, a second mounting groove is further provided in the accommodating cavity, the second mounting groove is communicated with the first mounting groove, part of the structure of the anti-wear gasket is located in the second mounting groove, and the radial dimension of the first mounting groove is smaller than the radial dimension of the second mounting groove.

[0017] In some embodiments, the thickness of the anti-wear pad is greater than the depth of the second mounting groove, so that a portion of the structure of the anti-wear pad extends out of the second mounting groove.

[0018] In some embodiments, the rotor assembly includes a driving rotor and a driven rotor, both of which are located in the accommodating cavity, and the transmission shaft is connected to the driving rotor; a limiting end surface is provided at one end of the driving rotor close to the anti-wear pad, and the limiting end surface is a plane, and the limiting end surface is against the anti-wear pad.

[0019] In some embodiments, a limiting portion is formed at one end of the active rotor away from the driven rotor, and the limiting end surface is formed on the limiting portion; a third mounting groove is also provided in the accommodating cavity, and the third mounting groove is communicated with the second mounting groove, and the limiting portion is located in the third mounting groove, and the radial dimension of the second mounting groove is smaller than the radial dimension of the third mounting groove.

[0020] In some embodiments, the anti-wear gasket is tightly 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 compressed, the size of the sealing ring along the axial direction of the transmission shaft is larger than the size of the first mounting groove along the axial direction of the transmission shaft.

[0021] In some embodiments, the sealing ring is a Y-shaped sealing ring, which includes a sealing ring body, and an inner lip and an outer lip are provided on one side of the sealing ring body, and the inner lip and the outer lip are against the partition.

[0022] In some embodiments, the pump housing includes a first shell and a second shell, the first shell and the second shell are connected, the first shell and the second shell jointly define the accommodating cavity, and the second shell defines the mounting cavity; the spherical rotor pump also includes a driving device, the driving device includes a main body and an output shaft connected to the main body, the main body is connected to the second shell, the output shaft is located in the mounting cavity and connected to the transmission shaft; the spherical rotor pump also includes a bearing, the bearing is located in the mounting cavity, the bearing is sleeved on the transmission shaft and / or the output shaft, the bearing is arranged on the side of the sealing ring away from the partition, and the bearing is in contact with the wall of the mounting cavity; the spherical rotor pump also includes a support block, the support block is arranged on the side of the bearing away from the partition, and the support block is fixed in the mounting cavity.

[0023] In some embodiments, the main body has an end face arranged toward the pump casing, the end face is formed with a protruding structure, the protruding structure is located in the mounting cavity, the support block is against the protruding structure; the radial dimension of the support block is larger than the radial dimension of the protruding structure.

[0024] In some embodiments, the active rotor includes a first support member and a first encapsulation, the first support member is wrapped inside the first encapsulation to serve as an inner skeleton of the active rotor, the transmission shaft extends into the first encapsulation and is connected to the first support member, wherein the transmission shaft is fixedly connected to the first support member, or the transmission shaft and the first support member are an integral structure; and / or, the driven rotor includes a second support member and a second encapsulation, the second encapsulation covers at least a portion of the second support member.

[0025] In some embodiments, the spherical rotor pump further includes a limiting structure, wherein the limiting structure is disposed between the transmission shaft and the pump housing, and the limiting structure is used to limit the movement of the transmission shaft relative to the pump housing along its own axial direction.

[0026] In some embodiments, the pump casing forms a limited position surface; the limiting structure includes a first component, a second component and a gasket, the first component is connected to the transmission shaft so that the first component is fixed relative to the transmission shaft along the axial direction of the transmission shaft, the second component is fixedly connected to the pump casing, the gasket abuts against the limiting surface, and the first component is limited between the gasket and the second component.

[0027] In some embodiments, the first component is a bearing sleeved on the transmission shaft; the bearing includes a bearing outer ring and a bearing inner ring connected to the bearing outer ring, the bearing inner ring is fastened to the transmission shaft, one end of the bearing outer ring abuts against the gasket, and the other end of the bearing outer ring abuts against the second component.

[0028] In some embodiments, the limiting structure further includes a third component, the third component is fixedly connected to the transmission shaft, and the third component abuts against an end of the bearing inner ring away from the gasket.

[0029] In some embodiments, the third component is a retaining spring sleeved on the transmission shaft or a pin fixedly installed on the transmission shaft.

[0030] In some embodiments, the first component is a retaining spring sleeved on the transmission shaft, or the first component is a pin fixedly mounted on the transmission shaft.

[0031] In some embodiments, the second component is a snap ring, and the snap ring is interference fit with the mounting cavity.

[0032] In some embodiments, the driving rotor and the driven rotor are connected via a pin shaft.

[0033] In some embodiments, the active rotor includes a first support member and a first encapsulated body, a portion of the structure of the first support member is wrapped inside the first encapsulated body to serve as an inner skeleton of the active rotor, and another portion of the structure of the first support member is located outside the first encapsulated body to form a connecting portion; the driven rotor includes a second support member and a second encapsulated body, the second encapsulated body covers at least a portion of the second support member, a through groove is provided on the second encapsulated body, the connecting portion extends into the interior of the second encapsulated body through the through groove, and is connected to the second support member through the pin shaft.

[0034] In some embodiments, the width of the through slot is greater than the width of the connecting portion, so that there is a distance between the connecting portion and the side wall of the through slot.

[0035] In some embodiments, the active rotor has a first axis, and the active rotor can rotate around the first axis relative to the pump housing. The driven rotor has a second axis, and the driven rotor can rotate around the second axis relative to the pump housing, and the first axis intersects with the second axis; a groove is provided on the driven rotor, and a pin shaft portion is formed on the active rotor, and the surface of the pin shaft portion is a cylindrical surface or a semi-cylindrical surface. The pin shaft portion is confined in the groove and can rotate around a third axis relative to the groove; the center axis of the pin shaft coincides with the third axis.

[0036] In some embodiments, the spherical rotor pump also includes a driving device and a constraint structure, the driving device has an output shaft, and the output shaft can drive the transmission shaft to rotate; the constraint structure is sleeved on the output shaft and the transmission shaft to keep the output shaft and the transmission shaft fixed.

[0037] In some embodiments, the output shaft and the constraint structure are both located in the installation cavity, a portion of the transmission shaft is located in the installation cavity, and another portion of the transmission shaft extends into the accommodating cavity; the constraint structure is a sleeve, and there is a distance between the outer wall surface of the sleeve and the wall surface of the installation cavity.

[0038] In some embodiments, the output shaft and the constraint structure are both located in the installation cavity, a portion of the transmission shaft is located in the installation cavity, and another portion of the transmission shaft extends into the accommodating cavity; the constraint structure is a bearing, the bearing is located in the installation cavity, and the outer wall surface of the bearing is in contact with the wall surface of the installation cavity.

[0039] In some embodiments, the driving device also includes a main body, and the output shaft is connected to the main body; a limited position surface is formed in the installation cavity, and the spherical rotor pump also includes a support block, which is located in the installation cavity and abuts against the main body, and the bearing is confined between the limit surface and the support block.

[0040] In some embodiments, the output shaft includes a first mating portion, the first mating portion is provided with a first contact surface, the transmission shaft includes a second mating portion, the second mating portion is provided with a second contact surface, and the first contact surface is tightly abutted against the second contact surface so that torque can be transmitted between the output shaft and the transmission shaft.

[0041] In some embodiments, the first contact surface and the second contact surface are both planar.

[0042] In some embodiments, the cross-sectional shape of the first matching portion is a first semicircle, the cross-sectional shape of the second matching portion is a second semicircle, and the radius of the first semicircle is equal to the radius of the second semicircle.

[0043] In some embodiments, the output shaft includes a third mating portion, the transmission 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, the mounting sleeve has an inner cavity, the shape of the inner cavity matches the prismatic structure, and the prismatic structure is matched with the inner cavity.

[0044] In some embodiments, one of the output shaft and the transmission shaft is provided with a slot, and the other of the output shaft and the transmission shaft is provided with a flat shaft portion, and the flat shaft portion cooperates with the slot to enable torque to be transmitted between the output shaft and the transmission shaft.

[0045] In some embodiments, one of the output shaft and the transmission shaft is further provided with a mounting hole extending axially, and the other of the output shaft and the transmission shaft is further provided with a mounting portion connected to the flat shaft portion, and the mounting portion is interference fit with the mounting hole.

[0046] In some embodiments, the spherical rotor pump also includes a seal; the pump housing includes a first shell and a second shell connected to the first shell, the first shell and the second shell jointly define the accommodating cavity, and the seal is located between the first shell and the second shell and is arranged around the accommodating cavity; a groove is provided on one of the first shell and the second shell, and a protrusion is provided on the other of the first shell and the second shell, the protrusion extends into the groove, and the end face of the protrusion abuts against the seal to press the seal into the groove.

[0047] In some embodiments, the thickness of the protrusion gradually decreases in a direction away from the rotor assembly.

[0048] In some embodiments, the protrusion is an annular structure, and the cross-sectional shape of the protrusion is a trapezoid.

[0049] In some embodiments, the active rotor has a first axis, and the active rotor can rotate around the first axis relative to the pump housing; the driven rotor has a second axis, and the driven rotor can rotate around the second axis relative to the pump housing, and the first axis intersects the second axis; the end face of the protrusion is perpendicular to the second axis, or the angle between the end face of the protrusion and the second axis is greater than 90° and less than or equal to 135°.

[0050] In some embodiments, the groove includes a first part and a second part that are connected to each other, the second part is located on a side of the first part away from the protrusion, the width of the first part is greater than the width of the second part, the protrusion is located in the first part, and the seal is located at least in the second part.

[0051] In some embodiments, the first shell and the second shell each include a shell body portion and a docking portion, the shell body portion having an open end, and the docking portion is located on the outside of the shell body portion and is arranged around the open end.

[0052] In some embodiments, the docking portion of the first shell and / or the docking portion of the second shell are provided with reinforcing ribs.

[0053] In some embodiments, the distance from the groove to the wall of the accommodating cavity is greater than or equal to 0.8 mm;

[0054] and / or, the distance from the groove to the outer surface of the docking portion is greater than or equal to 0.8 mm;

[0055] and / or, the distance from the bottom of the groove to the surface of the butt joint along the thickness direction is greater than or equal to 0.8 mm;

[0056] And / or, the width of the protrusion is greater than or equal to 0.8 mm.

[0057] In some embodiments, the distance from the groove to the outer surface of the docking portion is greater than the distance from the groove to the wall surface of the accommodating cavity.

[0058] In some embodiments, the seal is an annular seal, and the cross-sectional shape of the seal is circular.

[0059] In some embodiments, the driven rotor has a second axis, and the driven rotor can rotate around the second axis relative to the pump housing; the active rotor has a first axis, and the active rotor can rotate around the first axis relative to the pump housing, the driven rotor includes a base and a pin shaft portion arranged on the base, the active rotor is provided with a groove, the pin shaft portion is restricted in the groove and can rotate around a third axis relative to the groove; the pin shaft portion has a first mating surface and side surfaces located on both sides of the first mating surface, the first mating surface connects the two side surfaces, the first mating surface is an arc-shaped surface with a central angle less than or equal to 180°, and the minimum distance between the two side surfaces is equal to the chord length of the first mating surface.

[0060] In some embodiments, the two side surfaces are both planes, and the two side surfaces are arranged parallel to each other; or, the two side surfaces are both curved surfaces.

[0061] In some embodiments, both of the two side surfaces are planes, and an angle between a spatial plane where one of the side surfaces is located and a spatial plane where the other side surface is located is greater than 0° and less than or equal to 15°.

[0062] In some embodiments, the groove has a second mating surface and avoidance portions located on both sides of the second mating surface, the second mating surface is an arc-shaped surface, the second mating surface is used to cooperate with the first mating surface, and there is a gap between the avoidance portion and the pin shaft portion.

[0063] In some embodiments, the gap between the avoidance portion and the pin shaft portion gradually decreases along a direction approaching the second mating surface.

[0064] In some embodiments, the gap between the clearance portion and the pin shaft portion is greater than or equal to 0.05 mm and less than or equal to 0.6 mm.

[0065] In some embodiments, the base has two first planar portions facing the active rotor, and the two first planar portions are located on both sides of the pin shaft portion; the active rotor has two second planar portions facing the base, and the two second planar portions are arranged opposite to the two first planar portions one by one; the pin shaft portion, the wall surface of the accommodating cavity, the first planar portion and the corresponding second planar portion jointly define a variable cavity, and the volume of the variable cavity changes during the rotation of the pin shaft portion around the third axis relative to the groove.

[0066] In some embodiments, the end of the avoidance portion away from the second mating surface is the first end, the end of the avoidance portion close to the second mating surface is the second end, the line connecting the first end and the third axis is the first line, the line connecting the second end and the third axis is the second line, and there is a first angle between the first line and the second line; the end of the side surface away from the first mating surface is the third end, the end of the side surface close to the first mating surface is the fourth end, the line connecting the third end and the third axis is the third line, the line connecting the fourth end and the third axis is the fourth line, and there is a second angle between the third line and the fourth line; the first angle is greater than the second angle.

[0067] In some embodiments, the second angle is less than 40°.

[0068] In some embodiments, the spherical rotor pump has a first state, in which the volume of one of the two variable-volume chambers reaches a minimum value, and the volume of the other of the two variable-volume chambers reaches a maximum value; in the first state, the first planar portion and the corresponding second planar portion in any of the variable-volume chambers maintain a distance.

[0069] In some embodiments, a transition chamfer is formed between the clearance portion and the second planar portion.

[0070] In some embodiments, the first mating surface and the second mating surface are made of materials with the same expansion coefficient.

[0071] In some embodiments, the first mating surface and the second mating surface are made of the same material.

[0072] In some embodiments, the base also has an outer surface that matches the wall of the accommodating cavity, and the outer surface is a spherical surface; the end surfaces of both ends of the pin shaft portion along the third axis direction are spherical surfaces consistent with the outer surface.

[0073] In a second aspect, the present application provides a teeth cleaning device, which includes the spherical rotor pump in any of the above embodiments.

[0074] In the tooth cleaning device in the embodiment of the present application, the housing of the spherical rotor pump has a receiving chamber and a mounting chamber, the receiving chamber and the mounting chamber are separated by a partition, the rotor assembly is located in the receiving chamber, and the transmission shaft passes through a through hole on the partition to connect with the active rotor in the receiving chamber. The spherical rotor pump is also provided with a sealing ring, which is used to seal the gap between the transmission shaft and the hole wall of the through hole, or to seal the gap between the transmission shaft and the inner wall of the mounting chamber. In this way, even if there is a problem of gap sealing failure between the rotor assembly and the inner wall of the receiving chamber, the risk of liquid overflowing from the transmission shaft can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0075] Figure 1 A schematic diagram of the structure of a spherical rotor pump provided in one embodiment of the present application;

[0076] Figure 2 A schematic diagram of the structure of a spherical rotor pump provided in one embodiment of the present application from another perspective;

[0077] Figure 3 In one embodiment Figure 2 A schematic cross-sectional view of section AA of the structure shown;

[0078] Figure 4 In another embodiment Figure 2 A schematic cross-sectional view of section AA of the structure shown;

[0079] Figure 5 A schematic diagram of an isolation element provided in an embodiment of the present application;

[0080] Figure 6 A schematic diagram of the structure of a sealing ring provided in one embodiment of the present application;

[0081] Figure 7 A schematic cross-sectional view of a sealing ring provided in one embodiment of the present application;

[0082] Figure 8 A schematic diagram of the structure of a spherical rotor pump provided in another embodiment of the present application;

[0083] Fig. 9 A schematic structural diagram of a spherical rotor pump provided in another embodiment of the present application from another perspective;

[0084] Fig.10 for Fig. 9 A schematic cross-sectional view of section BB of the structure shown;

[0085] Fig.11 In another embodiment Figure 2 A schematic cross-sectional view of section AA of the structure shown;

[0086] Fig.12 An exploded schematic diagram of a spherical rotor pump provided in one embodiment of the present application;

[0087] Fig.13 An exploded schematic diagram of a partial structure of a spherical rotor pump provided in one embodiment of the present application;

[0088] Fig.14 A schematic diagram of the structure of a rotor assembly provided in one embodiment of the present application;

[0089] Fig.15 A schematic diagram of the structure of a driven rotor provided in one embodiment of the present application;

[0090] Fig.16 A schematic diagram of the structure of an active rotor provided in one embodiment of the present application;

[0091] Fig.17 A schematic diagram of the structure of a rotor assembly provided in one embodiment of the present application (the first colloid package and the second colloid package are omitted in the figure);

[0092] Fig.18 In another embodiment Figure 2 A schematic cross-sectional view of section AA of the structure shown;

[0093] Fig.19 In another embodiment Figure 7 A schematic cross-sectional view of section BB of the structure shown;

[0094] Fig. 20 A schematic diagram of the connection structure between the output shaft and the transmission shaft of a driving device provided in one embodiment of the present application;

[0095] Fig.21 A schematic diagram of a driving device provided in one embodiment of the present application;

[0096] Fig. 22 A schematic diagram of a transmission shaft provided in an embodiment of the present application;

[0097] Fig.23 A schematic diagram of the connection structure between the output shaft and the transmission shaft of a driving device provided in another embodiment of the present application;

[0098] Fig.24 A schematic diagram of a driving device provided in another embodiment of the present application;

[0099] Fig.25 A schematic diagram of a transmission shaft provided in another embodiment of the present application;

[0100] Fig.26 for Figure 3 A magnified schematic diagram of part B;

[0101] Fig. 27 for Figure 3 A partial enlarged schematic diagram of the structure shown (the seal is hidden);

[0102] Fig.28 for Fig. 27 A magnified schematic diagram of part C;

[0103] Fig.29 An exploded schematic diagram of a spherical rotor pump provided in one embodiment of the present application;

[0104] Fig.30 A schematic diagram of the structure of a first shell provided in an embodiment of the present application;

[0105] Fig.31 for Figure 3 A local enlarged schematic diagram in FIG.

[0106] Fig.32 is a schematic diagram of a rotor assembly in an embodiment of the present application;

[0107] Fig.33 is a schematic diagram of a driven rotor in an embodiment of the present application;

[0108] Fig.34 is a schematic diagram of a driven rotor in one embodiment of the present application from another viewing angle;

[0109] Fig.35 is a schematic diagram of an active rotor in an embodiment of the present application;

[0110] Fig.36 This is a schematic diagram of the structure of a teeth cleaning device provided in one embodiment of the present application.

[0111] Description of reference numerals:

[0112] 1000. Teeth cleaning device;

[0113] 100, spherical rotor pump; 200, body; 300, nozzle;

[0114] 1. Pump casing; 101. Accommodating cavity; 102. Mounting cavity; 103. Partition plate; 104. Through hole; 105. First placement groove; 106. Second placement groove; 107. First shell; 108. Second shell; 109. First section; 110. Second section; 111. Limiting surface; 121. Groove; 1211. First part; 1212. Second part; 122. Protrusion; 1221. End face; 131. Shell body; 132. Butt joint; 133. Reinforcement rib;

[0115] 2. Rotor assembly; 201. Active rotor; 202. Driven rotor; 2021. Second plane portion; 203. Variable volume cavity; 204. First support member; 2041. Connecting portion; 205. First colloid package; 206. Second support member; 207. Second colloid package; 2071. Through slot; 208. Pin shaft; 209. Pin shaft portion; 2091. First mating surface; 2092. Side surface; 2093. Third end; 2094. Fourth end; 2095. End surface; 210. Groove; 2101. Second mating surface; 2102. Avoidance portion; 2103. First end; 2104. Second end; 2105. Transition chamfer; 214. Base; 2141. First plane portion; 2142. Outer surface;

[0116] 3. transmission shaft; 301. second matching portion; 3011. second contact surface; 302. slot; 303. mounting hole;

[0117] 4. Sealing ring; 401. Sealing ring body; 402. Inner lip; 403. Outer lip;

[0118] 5. driving device; 501 output shaft; 5011, first matching portion; 5012, first contact surface; 5013, flat shaft portion; 5014, mounting portion; 502, main body portion; 503, end surface; 504, protruding structure;

[0119] 6. Bearing; 601. Bearing inner ring; 602. Bearing outer ring;

[0120] 7. Isolation piece; 701. Avoidance gap;

[0121] 8. Anti-wear pad;

[0122] 9. Support block;

[0123] 10. Limiting structure; 1001. First component; 1002. Second component; 1003. Third component; 1004. Gasket;

[0124] 11. Circlip;

[0125] 12. Snap ring;

[0126] 13. Constraint structure;

[0127] 14. Sleeve;

[0128] 16. Seals;

[0129] 23. Gasket. DETAILED DESCRIPTION

[0130] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0131] In the description of this application, it should be understood that if the terms "upper", "lower", "left", "right", etc. indicate an orientation or positional relationship based on the orientation or positional relationship shown in the drawings, it is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes and cannot be understood as a limitation on this patent. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0132] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as suggesting or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0133] In the description of this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0134] A spherical rotor pump is a positive displacement liquid delivery device. It usually includes a pump housing and a rotor assembly disposed in the pump housing. The function of pumping water can be achieved through the rotation of the rotor assembly. When the spherical rotor pump is working, the rotor assembly in the pump housing rotates at high speed. The precise fit between the rotor assembly and the pump housing is a necessary condition for sealing the gap inside the pump. Therefore, the parts of the spherical rotor pump are usually processed by precision manufacturing.

[0135] However, the precision manufacturing processing method also brings problems such as complex processes, long manufacturing cycles, and high costs. Some manufacturers have changed some parts to mold batch manufacturing, thereby simplifying the process, improving production efficiency, and reducing costs. However, due to the reduced precision of the parts, the gap seal failure in the pump is prone to occur. When the gap seal fails, the liquid in the pump is likely to overflow from the transmission shaft during the movement of the rotor assembly relative to the pump housing, resulting in leakage.

[0136] Based on this, an embodiment of the first aspect of the present application provides a spherical rotor pump, which aims to reduce the risk of liquid in the pump overflowing from the transmission shaft.

[0137] like Figure 1 , Figure 2 as well as Figure 3 As shown, the spherical rotor pump 100 provided by the first embodiment of the present application includes a pump housing 1, a rotor assembly 2, a transmission shaft 3 and a sealing ring 4. The pump housing 1 has a receiving chamber 101 and a mounting chamber 102, and the receiving chamber 101 and the mounting chamber 102 are separated by a partition 103, and the partition 103 is provided with a through hole 104. The rotor assembly 2 includes an active rotor 201 and a driven rotor 202, and the active rotor 201 and the driven rotor 202 are both located in the receiving chamber 101. The active rotor 201, the driven rotor 202 and the wall surface of the receiving chamber 101 jointly define a variable volume chamber 203, and the active rotor 201 can drive the driven rotor 202 to rotate, and when the active rotor 201 drives the driven rotor 202 to rotate, the volume of the variable volume chamber 203 changes. The transmission shaft 3 is penetrated by the through hole 104, a part of the transmission shaft 3 is located in the mounting chamber 102, and another part of the transmission shaft 3 extends into the receiving chamber 101 and is connected to the active rotor 201. The sealing ring 4 is used to seal the gap between the transmission shaft 3 and the hole wall of the through hole 104 , or to seal the gap between the transmission shaft 3 and the inner wall of the installation cavity 102 .

[0138] Specifically, the transmission shaft 3 is used to connect with the driving device 5, and the driving device 5 can provide power. When the driving device 5 is working, it can drive the active rotor 201 to rotate through the transmission shaft 3. In the process of the active rotor 201 driving the driven rotor 202 to rotate, the position and volume of the variable cavity 203 change. Usually, a liquid inlet and a liquid outlet are provided on the pump housing 1. As the rotor assembly 2 rotates, the same variable cavity 203 will alternately connect the liquid inlet and the liquid outlet. Moreover, the volume of the variable cavity 203 when it is connected to the liquid inlet is greater than the volume when it is connected to the liquid outlet. Therefore, as the variable cavity 203 rotates from the position connected to the liquid inlet to the position connected to the liquid outlet, the pressure in the accommodating chamber 101 will rise, thereby driving the liquid to be pumped out from the liquid outlet.

[0139] The spherical rotor pump 100 in the embodiment of the present application has a housing having a housing chamber 101 and a mounting chamber 102, the housing chamber 101 and the mounting chamber 102 are separated by a partition 103, the rotor assembly 2 is located in the housing chamber 101, and the transmission shaft 3 passes through a through hole 104 on the partition 103 to connect with the active rotor 201 in the housing chamber 101. The spherical rotor pump 100 is also provided with a sealing ring 4, which is used to seal the gap between the transmission shaft 3 and the hole wall of the through hole 104, or to seal the gap between the transmission shaft 3 and the inner wall of the mounting chamber 102. In this way, even if there is a problem of gap sealing failure between the rotor assembly 2 and the inner wall of the housing chamber 101, the risk of liquid overflowing from the transmission shaft 3 can be reduced.

[0140] In some embodiments, Figure 3 As shown, the sealing ring 4 is arranged in the installation cavity 102, and the sealing ring 4 is sleeved on the transmission shaft 3. In this way, the sealing ring 4 seals one side of the installation cavity 102 to reduce the risk of liquid overflow.

[0141] Specifically, the sealing ring 4 may abut against the partition plate 103 , thereby sealing the gap between the transmission shaft 3 and the through hole 104 .

[0142] Alternatively, the sealing ring 4 may also maintain a certain distance from the partition 103 . In this case, the sealing ring 4 may abut against the inner wall of the installation cavity 102 , thereby sealing the gap between the transmission shaft 3 and the inner wall of the installation cavity 102 .

[0143] Furthermore, if Figure 3 As shown, the spherical rotor pump 100 may also include a bearing 6 and a spacer 7, wherein the bearing 6 is located in the installation cavity 102, the bearing 6 is sleeved on the transmission shaft 3, the bearing 6 is arranged on the side of the sealing ring 4 away from the partition 103, the bearing 6 contacts the wall of the installation cavity 102, and the spacer 7 is located between the bearing 6 and the sealing ring 4. By setting the bearing 6 sleeved on the transmission shaft 3 and making the bearing 6 contact the wall of the installation cavity 102, the centering accuracy of the transmission shaft 3 during installation can be improved by the bearing 6. In addition, in the process of the driving device 5 driving the transmission shaft 3 to rotate, it can also ensure that the position of the transmission shaft 3 does not shift, thereby improving the position stability of the transmission shaft 3. In addition, the spacer 7 is used to isolate the bearing 6 and the sealing ring 4, so that it can be ensured that the bearing 6 will not affect the sealing ring 4 when it moves, thereby avoiding the displacement of the sealing ring 4 and affecting the sealing performance.

[0144] Furthermore, if Figure 3As shown, the installation cavity 102 includes a first section 109 and a second section 110 which are connected to each other, and the second section 110 is located on the side of the first section 109 away from the partition 103; the cross-sectional area of ​​the second section 110 is larger than the cross-sectional area of ​​the first section 109, so that the connection position of the second section 110 and the first section 109 forms a step-shaped limiting surface 111, the sealing ring 4 is located in the first section 109, the bearing 6 and the isolation member 7 are both located in the second section 110, and the isolation member 7 is against the limiting surface 111.

[0145] Since the cross-sectional area of ​​the second section 110 of the installation cavity 102 is larger than the cross-sectional area of ​​the first section 109, the sealing ring 4 is located in the first section 109 with a smaller cross-sectional area, which is conducive to putting the sealing ring 4 in a compressed state, so that the sealing performance can be better exerted. In addition, the connection position of the second section 110 and the first section 109 forms a stepped limiting surface 111, and the isolation members 7 are all located in the second section 110 and the isolation members 7 are against the limiting surface 111. In this way, the blocking effect of the isolation member 7 on the sealing member can prevent the sealing member from escaping from the first part. On the other hand, the limiting effect of the limiting surface 111 is also conducive to preventing the isolation member 7 from excessively squeezing the sealing ring 4, thereby causing excessive friction between the sealing ring 4 and the transmission shaft 3.

[0146] Specifically, the isolation member 7 is tightly against the sealing ring 4 so that the sealing ring 4 is compressed along the axial direction of the transmission shaft 3; wherein, before the sealing ring 4 is compressed, the dimension of the sealing ring 4 along the axial direction of the transmission shaft 3 is greater than the dimension of the first section 109 along the axial direction of the transmission shaft 3.

[0147] It can be understood that when the sealing ring 4 is not compressed (under a natural state), its dimension along the axial direction of the transmission shaft 3 is larger than the dimension of the first section 109 along the axial direction of the transmission shaft 3. When the sealing ring 4 is installed in the first section 109, the sealing ring 4 is compressed in the axial direction of the transmission shaft 3 and is squeezed and deformed, which is conducive to improving the sealing performance of the sealing ring 4.

[0148] In one embodiment, Figure 3 , Figure 5 As shown, 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 tightly sleeved on the transmission shaft 3. The isolation member 7 is an annular gasket. The inner diameter of the gasket is smaller than the outer diameter of the bearing inner ring 601. An avoidance notch 701 is formed on the side of the gasket close to the bearing 6. The avoidance notch 701 is arranged opposite to the bearing inner ring 601 to avoid the bearing inner ring 601.

[0149] It is understandable that when the transmission shaft 3 rotates, the bearing inner ring 601 rotates with the transmission shaft 3, and the bearing outer ring 602 remains fixed. When the isolating member 7 is an annular gasket, and the inner diameter of the gasket is smaller than the outer diameter of the bearing inner ring 601, the gasket and the bearing inner ring 601 can be prevented from contacting by providing an avoidance notch 701 on the side of the gasket close to the bearing 6, so that the wall bearing inner ring 601 rubs against the gasket when rotating.

[0150] 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 on the transmission shaft 3, and the isolation member 7 is an annular gasket, the inner diameter of the gasket is larger than the outer diameter of the bearing inner ring 601, so that the gasket and the bearing inner ring 601 are spaced apart in the radial direction.

[0151] When the spacer 7 is an annular gasket, and the inner diameter of the gasket is larger than the outer diameter of the bearing inner ring 601, a gap can be maintained between the gasket and the bearing inner ring 601 in the radial direction, so that the gasket does not contact the bearing inner ring 601. In this way, friction between the bearing inner ring 601 and the gasket can be avoided when the bearing inner ring 601 rotates.

[0152] In other embodiments, Figure 4 As shown, the sealing ring 4 is arranged in the accommodating cavity 101, and the sealing ring 4 is sleeved on the transmission shaft 3 and abuts against the partition 103. In this way, the sealing ring 4 seals the gap between the transmission shaft 3 and the hole wall of the through hole 104 on one side of the accommodating cavity 101 to reduce the risk of liquid overflowing into the installation cavity 102.

[0153] Furthermore, a first placement groove 105 may be provided in the accommodating cavity 101, and the sealing ring 4 is located in the first placement groove 105. Thus, the sealing ring 4 is limited by the first placement groove 105, so as to help the sealing ring 4 maintain position stability.

[0154] Furthermore, if Figure 4 As shown, the spherical rotor pump 100 may further include an anti-wear pad 8, which is disposed between the active rotor 201 and the sealing ring 4. The anti-wear pad 8 separates the sealing ring 4 from the active rotor 201, thereby preventing the active rotor 201 from rubbing against the sealing ring 4 when rotating, thereby preventing the sealing ring 4 from being worn or shifted.

[0155] Furthermore, a second placement groove 106 is further provided in the accommodating cavity 101, the second placement groove 106 is communicated with the first placement groove 105, a part of the structure of the anti-wear gasket 8 is located in the second placement groove 106, and the radial dimension of the first placement groove 105 is smaller than the radial dimension of the second placement groove 106. In this way, the anti-wear gasket 8 can be limited by the second installation groove, so that the anti-wear gasket 8 maintains position stability, and in addition, the blocking effect of the anti-wear gasket 8 on the sealing ring 4 can also be utilized to keep the sealing ring 4 in the first placement groove 105 at all times.

[0156] Furthermore, the thickness of the anti-wear pad 8 is greater than the depth of the second placement groove 106, so that part of the structure of the anti-wear pad 8 extends out of the second placement groove 106. In this way, the rotor assembly 2 abuts against the part of the anti-wear pad 8 extending out of the second placement groove 106, so that part of the anti-wear pad 8 is pressed tightly in the second placement groove 106, and the pressed anti-wear pad 8 further presses the sealing ring 4 in the first placement groove 105. In this way, the sealing ring 4 can be tightly abutted against the partition 103 to improve the sealing performance of the sealing ring 4.

[0157] Furthermore, if Figure 3 , Figure 4 As shown, the rotor assembly 2 includes a driving rotor 201 and a driven rotor 202, both of which are located in the accommodating chamber 101, and the transmission shaft 3 is connected to the driving rotor 201. A limiting end face is provided at one end of the driving rotor 201 close to the anti-wear pad 8, the limiting end face is a plane, and the limiting end face abuts against the anti-wear pad 8. In this embodiment, a limiting end face is provided at one end of the driving rotor 201 close to the anti-wear pad 8, the limiting end face is a plane and abuts against the anti-wear pad 8, thereby improving the force uniformity of the anti-wear pad 8.

[0158] Furthermore, if Figure 3 , Figure 4 As shown, a limiting portion 2012 is formed at one end of the active rotor 201 away from the driven rotor 202, and a limiting end surface is formed on the limiting portion 2012. A third placement groove 141 is also provided in the accommodating chamber 101, the third placement groove 141 is communicated with the second placement groove 106, the limiting portion 2012 is located in the third placement groove 141, and the radial dimension of the second placement groove 106 is smaller than the radial dimension of the third placement groove 141. By forming the limiting portion 2012 on the active rotor 201 and locating the limiting portion 2012 in the third placement groove 141, it is beneficial for the active rotor 201 to maintain a preset posture in the accommodating chamber 101, and to avoid the active rotor from generating unexpected rotational motion.

[0159] In some embodiments, the anti-wear gasket 8 is tightly against the sealing ring 4 so that the sealing ring 4 is compressed along the axial direction of the transmission shaft 3; wherein, before the sealing ring 4 is compressed, the size of the sealing ring 4 along the axial direction of the transmission shaft 3 is greater than the size of the first mounting groove 105 along the axial direction of the transmission shaft 3.

[0160] It can be understood that when the sealing ring 4 is not compressed (in a natural state), its dimension along the axial direction of the transmission shaft 3 is larger than the dimension of the first placement groove 105 along the axial direction of the transmission shaft 3. When the sealing ring 4 is installed in the first placement groove 105, the sealing ring 4 is compressed in the axial direction of the transmission shaft 3 and is squeezed and deformed, which is conducive to improving the sealing performance of the sealing ring 4.

[0161] In some embodiments, Figure 6 , Figure 7 As shown, the sealing ring 4 is a Y-shaped sealing ring, which includes a sealing ring body 401, and an inner lip 402 and an outer lip 403 are provided on one side of the sealing ring body 401, and the inner lip 402 and the outer lip 403 are against the partition 103. When the Y-shaped sealing ring 4 is squeezed and deformed, the inner lip 402 and the outer lip 403 are deformed more than the sealing ring body 401. In this embodiment, the inner lip 402 and the outer lip 403 of the sealing ring 4 are against the partition 103, so that the sealing performance between the sealing ring 4 and the partition 103 is better, thereby further reducing the possibility of the liquid in the accommodating cavity 101 leaking through the through hole 104.

[0162] In some embodiments, the pump housing 1 includes a first housing 107 and a second housing 108, the first housing 107 and the second housing 108 are connected, the first housing 107 and the second housing 108 jointly define a receiving cavity 101, and the second housing 108 defines a mounting cavity 102. The spherical rotor pump 100 also includes a driving device 5, the driving device 5 includes a main body 502 and an output shaft 501 connected to the main body 502, the main body 502 is connected to the second housing 108, and the output shaft 501 is located in the mounting cavity 102 and connected to the transmission shaft 3.

[0163] In some embodiments, Figure 8 , Fig. 9 as well as Fig.10 As shown, the spherical rotor pump 100 further includes a bearing 6, which is located in the installation cavity 102, and is sleeved on the transmission shaft 3 and / or the output shaft 501. The bearing 6 is arranged on the side of the sealing ring 4 away from the partition 103, and the bearing 6 contacts the wall surface of the installation cavity 102. The spherical rotor pump 100 further includes a support block 9, which is arranged on the side of the bearing 6 away from the partition 103, and the support block 9 is fixed in the installation cavity 102.

[0164] Among them, the driving device 5 can be a motor, and the output shaft 501 of the driving device 5 is located in the installation cavity 102 and connected to the transmission shaft 3. In this way, the installation cavity 102 can form a protective effect on the output shaft 501 and the transmission shaft 3 to prevent external debris from touching the output shaft 501 or the transmission shaft 3 and affecting the structural stability and transmission performance of the two.

[0165] In addition, by sleeve-mounting the bearing 6 on the transmission shaft 3 and / or the output shaft 501 and making the bearing 6 contact the wall of the mounting cavity 102, the centering accuracy of the transmission shaft 3 and / or the output shaft 501 during installation can be improved. In addition, in the process of the driving device 5 driving the transmission shaft 3 to rotate, it can also ensure that the position of the transmission shaft 3 and / or the output shaft 501 does not shift, thereby improving the position stability of the transmission shaft 3 and / or the output shaft 501.

[0166] In addition, the spherical rotor pump 100 further includes a support block 9, which is disposed on a side of the bearing 6 away from the partition 103, and is fixed in the mounting cavity 102. The support block 9 can block external debris on the side of the bearing 6 away from the partition 103, thereby preventing the external debris from contacting the bearing 6 and causing an adverse effect on the performance of the bearing 6.

[0167] In some embodiments, the main body 502 has an end face 503 set toward the pump casing 1, and a protrusion structure 504 is formed on the end face 503. The protrusion structure 504 is located in the installation cavity 102, and the support block 9 is against the protrusion structure 504; the radial dimension of the support block 9 is larger than the radial dimension of the protrusion structure 504.

[0168] By making the support block 9 abut against the protruding structure 504 on the end of the main body 502, the support block 9 and the protruding structure 504 together form a blocking structure for blocking external debris, which can not only block solid debris, but also has a certain blocking effect on liquid debris, thereby better protecting the bearing 6. In addition, the radial dimension of the support block 9 is larger than the radial dimension of the protruding structure 504, which is conducive to reducing the contact area between the two, thereby increasing the pressure between the two, and making the contact between the two closer.

[0169] In addition, the protruding structure 504 can be used to compress the support block 9 and the bearing 6 so that the bearing 6 and the isolation member 7 are tightly pressed against each other, so that the isolation member 7, the bearing 6 and the support block 9 are all firmly installed along the axial direction of the transmission shaft 3.

[0170] In some embodiments, Figure 3 or Figure 4As shown, the active rotor 201 includes a first support member 204 and a first encapsulation body 205 . The first support member 204 is encapsulated inside the first encapsulation body 205 to serve as an inner skeleton of the active rotor 201 . The transmission shaft 3 extends into the first encapsulation body 205 and is connected to the first support member 204 .

[0171] In this embodiment, the active rotor 201 includes a first support member 204 and a first encapsulated body 205 wrapped outside the first support member 204. The first support member 204 can be made of a material with high strength, such as a metal material. Thus, the overall structural strength of the active rotor 201 can be improved, and the first encapsulated body 205 can better form a gap seal with the inner wall of the pump housing 1. On this basis, the transmission shaft 3 extends into the first encapsulated body 205 and is connected to the first bearing 6, which is conducive to improving the connection strength between the transmission shaft 3 and the active rotor 201, thereby improving the stability of the transmission.

[0172] It is understandable that the transmission shaft 3 may also be made of a material with higher strength, such as a metal material, so that the transmission shaft 3 has better structural strength, thereby being able to transmit more stably.

[0173] Furthermore, the transmission shaft 3 can be fixedly connected to the first support member 204, that is, the two can be manufactured separately and then connected by screw connection, rivet connection, welding, etc. Alternatively, the transmission shaft 3 and the first support member 204 are an integrated structure, that is, the two can be processed and formed by the same manufacturing process (such as metal casting).

[0174] In some embodiments, the driven rotor 202 includes a second support member 206 and a second encapsulated body 207, and the second encapsulated body 207 covers at least a portion of the second support member 206. In this embodiment, the driven rotor 202 includes a second support member 206 and a second encapsulated body 207 that covers at least a portion of the second support member 206, and the second support member 206 can be made of a material with high strength, such as a metal material. Thus, the overall structural strength of the driven rotor 202 can be improved, and the second encapsulated body 207 can better form a gap seal with the inner wall of the pump housing 1.

[0175] In some embodiments, Fig.11 As shown, the spherical rotor pump 100 further includes a limiting structure 10 , which is disposed between the transmission shaft 3 and the pump housing 1 , and is used to limit the movement of the transmission shaft 3 relative to the pump housing 1 along its own axial direction.

[0176] Due to the limitation of machining accuracy, there may be movable space after the rotor assembly 2 and the pump housing 1 are assembled, which makes the rotor assembly 2 easy to move in the axial direction, thereby increasing the friction between the rotor assembly 2 and the pump housing 1.

[0177] In this embodiment, a limiting structure 10 is provided between the transmission shaft 3 and the pump housing 1. The limiting structure 10 can limit the movement of the transmission shaft 3 relative to the pump housing 1 along its own axial direction. Since the transmission shaft 3 is connected to the active rotor 201 in the rotor assembly 2, the movement of the active rotor 201 along the axial direction of the transmission shaft 3 can be further limited to reduce the possibility of axial movement of the active rotor 201, thereby improving the problem of axial movement of the rotor assembly 2.

[0178] In some embodiments, Fig.11 As shown, the pump housing 1 forms a limited position surface 111, and the limiting structure 10 includes a first component 1001, a second component 1002, and a gasket 1004. The first component 1001 is connected to the transmission shaft 3 so that the first component 1001 is fixed relative to the transmission shaft 3 along the axial direction of the transmission shaft 3, the second component 1002 is fixedly connected to the pump housing 1, the gasket 1004 abuts against the limited position surface 111, and the first component 1001 is limited between the gasket 1004 and the second component 1002.

[0179] The first component 1001 is restricted between the gasket 1004 and the second component 1002, so that the movement of the first component 1001 along the axis direction of the transmission shaft 3 is restricted. Because the first component 1001 is connected to the transmission, the movement of the transmission shaft 3 relative to the pump housing 1 along its own axis direction is restricted.

[0180] In one embodiment, Fig.11 As shown, the first component 1001 is a bearing 6 sleeved on the transmission shaft 3. In this embodiment, the bearing 6 sleeved on the transmission shaft 3 is restricted between the gasket 1004 and the second component 1002, thereby restricting the movement of the transmission shaft 3 along its own axis. In addition, the bearing 6 can contact the wall surface of the pump housing 1, so that the centering accuracy of the transmission shaft 3 during installation can be improved by the bearing 6. In addition, in the process of the driving device 5 driving the transmission shaft 3 to rotate, it can also ensure that the position of the transmission shaft 3 does not deviate, thereby improving the position stability of the transmission shaft 3.

[0181] 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 transmission shaft 3, so that the bearing 6 is fixed relative to the transmission shaft 3 along the axial direction of the transmission shaft 3. One end of the bearing outer ring 602 abuts against the gasket 1004, and the other end of the bearing outer ring 602 abuts against the second component 1002, that is, the bearing outer ring 602 is restricted between the gasket 1004 and the second component 1002. Thus, the movement of the transmission shaft 3 relative to the pump housing 1 along its own axial direction is restricted.

[0182] Furthermore, if Fig.11As shown, the limiting structure 10 may further include a third member 1003, the third member 1003 is fixedly connected to the transmission shaft 3, and the third member 1003 abuts against one end of the bearing inner ring 601 away from the gasket 1004. By providing the third member 1003, the axial stability between the transmission shaft 3 and the bearing 6 can be further ensured, and the tight fit between the bearing inner ring 601 and the transmission shaft 3 is prevented from loosening, thereby causing the transmission shaft 3 to move relative to the bearing 6.

[0183] Specifically, the third member 1003 can be a retaining spring 11 sleeved on the transmission shaft 3, which has the advantage of easy installation. In other embodiments, the third member 1003 can also be a pin fixedly installed on the transmission shaft 3. Using the pin as the third member 1003 has the advantage of stable connection.

[0184] In another embodiment, the first member 1001 is a retaining 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 transmission shaft 3, and at this time, the retaining spring 11 or the pin sleeved on the transmission shaft 3 is restricted between the gasket 1004 and the second member 1002, thereby restricting the movement of the transmission shaft 3 along its own axial direction.

[0185] In some embodiments, Fig.11 As shown, the second component 1002 is a snap ring 12 fixedly connected to the pump housing 1. Using the snap ring 12 as the second component 1002 has the advantages of easy installation, convenient material acquisition, and low cost.

[0186] Furthermore, if Fig.11 As shown, the pump housing 1 also has an installation cavity 102, the limiting structure 10 is located in the installation 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 installation cavity 102, and the snap ring 12 is interference fit with the installation cavity 102. In this embodiment, the pump housing 1 has an accommodating cavity 101 and an installation cavity 102, the accommodating cavity 101 is used to accommodate the rotor assembly 2, and the installation cavity 102 can be used to accommodate the output shaft 501 of the drive device 5, so that the installation cavity 102 can be used to protect the output shaft 501 of the drive device 5. 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 also be under the protection of the installation cavity 102, so that external debris will not touch the output shaft 501, the transmission shaft 3, the limiting structure 10, etc. On this basis, the snap ring 12 can be interference fit with the installation cavity 102 to achieve a fixed connection between the second component 1002 (snap ring 12) and the pump housing 1.

[0187] In some embodiments, Fig.11 , Fig.12 , Fig.13 as well as Fig.14 As shown, the driving rotor 201 and the driven rotor 202 are connected by a pin shaft 208, so that the driven rotor 202 can rotate around the pin shaft 208 relative to the driving rotor 201. In this embodiment, the driving rotor 201 and the driven rotor 202 are connected by the pin shaft 208, so that the driving rotor 201 and the driven rotor 202 are connected together. In this way, the driving rotor 201 and the driven rotor 202 become an integral structure. In this way, on the basis of the limiting structure 10 limiting the movement of the transmission shaft 3 relative to the pump housing 1 along its own axis direction, the possibility of the driving rotor 201 and the driven rotor 202 being moved can be reduced, thereby improving the position stability of the driving rotor 201 and the driven rotor 202 relative to the pump housing 1.

[0188] In some embodiments, Fig.11 , Fig.15 , Fig.16 as well as Fig.17 As shown, the active rotor 201 includes a first support member 204 and a first encapsulated body 205, a part of the structure of the first support member 204 is wrapped inside the first encapsulated body 205 to serve as the inner skeleton of the active rotor 201, and another part of the structure of the first support member 204 is located outside the first encapsulated body 205 to form a connecting portion 2041. The driven rotor 202 includes a second support member 206 and a second encapsulated body 207, and the second encapsulated body 207 covers at least a part of the second support member 206. The second encapsulated body 207 is provided with a through slot 2071, and the connecting portion 2041 extends into the interior of the second encapsulated body 207 through the through slot 2071, and is connected to the second support member 206 through a pin 208.

[0189] In this embodiment, the active rotor 201 includes a first support member 204 and a first encapsulated body 205. The first support member 204 can be made of a material with high strength, thereby improving the overall structural strength of the active rotor 201. The outside of the active rotor 201 is the first encapsulated body 205, and the first encapsulated body 205 can better form a gap seal with the inner wall of the pump housing 1. Similarly, the driven rotor 202 includes a second support member 206 and a second encapsulated body 207. The second support member 206 can be made of a material with high strength, thereby improving the overall structural strength of the driven rotor 202. The outside of the driven rotor 202 is the second encapsulated body 207, and the second encapsulated body 207 can better form a gap seal with the inner wall of the pump housing 1.

[0190] In addition, a part of the structure of the first support member 204 is wrapped inside the first encapsulated body 205, and another part of the structure is located outside the first encapsulated body 205 to form a connecting portion 2041. A through slot 2071 is provided on the second encapsulated body 207, and the connecting portion 2041 extends into the interior of the second encapsulated body 207 through the through slot 2071, and is connected to the second support member 206 through a pin 208. In this way, the first support member 204 and the second support member 206 are connected through the pin 208, thereby realizing the connection between the active rotor 201 and the driven rotor 202, so that the active rotor 201 and the driven rotor 202 form an integral structure.

[0191] Furthermore, if Fig.11 As shown, the width of the through slot 2071 is greater than the width of the connecting portion 2041, so that there is a gap between the connecting portion 2041 and the side wall of the through slot 2071. In this way, the connecting portion 2041 has a certain swing space, so that when the active rotor 201 drives the driven rotor 202 to rotate, the connecting portion 2041 can be prevented from interfering with the second encapsulated body 207.

[0192] In some embodiments, Fig.12 As shown, the active rotor 201 has a first axis a, and the active rotor 201 can rotate around the first axis a relative to the pump housing 1. The driven rotor 202 has a second axis b, and the driven rotor 202 can rotate around the second axis b relative to the pump housing 1. The first axis a intersects with the second axis b; the pin 208 intersects with both the first axis a and the second axis b.

[0193] In this embodiment, the first axis a of the active rotor 201 intersects with the second axis b of the driven rotor 202, and the pin 208 intersects with both the first axis a and the second axis b. When the active rotor 201 drives the driven rotor 202 to rotate, the active rotor 201 rotates continuously around the first axis, and the driven rotor 202 rotates continuously around the second axis b. At the same time, the driven rotor 202 performs reciprocating swinging motion around the pin 208. In this process, the volume of the variable capacity cavity 203 defined by the active rotor 201, the driven rotor 202 and the wall of the accommodating cavity 101 can be changed.

[0194] In some embodiments, Fig.12 , Fig.14 , Fig.15 as well as Fig.16 As shown, a groove 210 is provided on the driven rotor 202, and a pin shaft portion 209 is formed on the active rotor 201. The surface of the pin shaft portion 209 is a cylindrical surface or a semi-cylindrical surface. The pin shaft portion 209 is confined in the groove 210 and can rotate around the third axis c relative to the groove 210; the central axis of the pin shaft 208 coincides with the third axis c.

[0195] Through the cooperation of the pin shaft portion 209 and the groove 210, a seal can be formed between the active rotor 201 and the driven rotor 202, so that the active rotor 201, the driven shaft and the wall of the accommodating chamber 101 can define a sealed variable cavity 203. In addition, the pin shaft portion 209 is restricted 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. On this basis, the central axis of the pin shaft 208 is made to coincide with the third axis c, so that during the process of the driven rotor 202 making a reciprocating swinging motion around the pin shaft 208, the pin shaft portion 209 can always be in a good cooperation state with the groove 210, so that a good seal can be maintained between the active rotor 201 and the driven rotor 202. On the other hand, coinciding the central axis of the pin shaft 208 with the third axis c is also conducive to smooth movement of the rotor assembly 2 and prevents movement jamming.

[0196] In some embodiments, the spherical rotor pump 100 further includes a driving device 5 and a constraint structure 13. The driving device 5 has an output shaft 501, and the output shaft 501 can drive the transmission shaft 3 to rotate. The constraint structure 13 is sleeved on the output shaft 501 and the transmission shaft 3 to keep the output shaft 501 and the transmission shaft 3 fixed.

[0197] The spherical rotor pump in the related art is prone to the phenomenon of the rotor assembly not rotating smoothly, and in severe cases, the pump may get stuck. The main reason for the rotor assembly not rotating smoothly in the spherical rotor pump in the related art is that the coaxiality between the output shaft of the drive device and the transmission shaft is poor, which causes the rotor assembly to deviate from the expected position, thereby causing the rotor assembly to rotate smoothly, and in severe cases, it may cause the pump to get stuck. In addition, when the rotor assembly deviates from the expected position, the friction between the rotor assembly and the pump housing will also increase.

[0198] The spherical rotor pump 100 in this embodiment is provided with a constraint structure 13, which is sleeved on the transmission shaft 3 and the output shaft 501 of the driving device 5 to keep the output shaft 501 and the transmission shaft 3 fixed. The holding effect of the constraint structure 13 can improve the coaxiality between the output shaft 501 of the driving device 5 and the transmission shaft 3. Thus, 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, which is conducive to avoiding the problem of pump jamming and the problem of increased friction between the rotor assembly 2 and the pump housing 1.

[0199] Furthermore, if Fig.18As shown, the pump housing 1 also has an installation cavity 102, the output shaft 501 and the constraint structure 13 are both located in the installation cavity 102, a portion of the transmission shaft 3 is located in the installation cavity 102, and another portion of the transmission shaft 3 extends into the accommodating cavity 101. The constraint structure 13 is a sleeve 14, and there is a gap between the outer wall surface of the sleeve 14 and the wall surface of the installation cavity 102.

[0200] In this embodiment, the pump housing 1 has a receiving chamber 101 and a mounting chamber 102. The receiving chamber 101 is used to receive the rotor assembly 2, and the mounting chamber 102 can be used to receive the output shaft 501 of the drive device 5. In this way, the output shaft 501 of the drive device 5 can be protected by the mounting chamber 102. At the same time, the constraint structure 13 and a part of the transmission shaft 3 are also located in the mounting chamber 102, so that the constraint structure 13 and the transmission shaft 3 can also be protected by the mounting chamber 102. In addition, in this embodiment, the constraint structure 13 is a sleeve 14 sleeved on the output shaft 501 and the transmission shaft 3, and the sleeve 14 can keep the axis of the output shaft 501 and the axis of the transmission shaft 3 in the same line. In addition, there is a gap between the outer wall of the sleeve 14 and the wall of the mounting chamber 102, so that the sleeve 14 will not generate friction with the wall of the mounting chamber 102 when rotating with the output shaft 501 and the transmission shaft 3.

[0201] Furthermore, if Fig.18 As shown, the spherical rotor pump 100 may further include a bearing 6 sleeved on the transmission shaft 3, the bearing 6 being located in the mounting cavity 102, and the outer wall surface of the bearing 6 being in contact with the wall surface of the mounting cavity 102. By providing the bearing 6 sleeved on the transmission shaft 3 and making the bearing 6 in contact with the wall surface of the mounting cavity 102, the centering accuracy of the transmission shaft 3 relative to the mounting cavity 102 can be improved, thereby further improving the position accuracy of the transmission shaft 3. In addition, in the process of the driving device 5 driving the transmission shaft 3 to rotate, the position of the transmission shaft 3 can also be kept from being offset.

[0202] Furthermore, if Fig.18 As shown, a limited surface 111 is formed in the installation cavity 102, and the spherical rotor pump 100 further includes a snap ring 12, a gasket 23 and a snap spring 11. The gasket 23 abuts against the limited surface 111, the snap ring 12 is interference fit with the installation cavity 102, and the snap spring 11 is sleeved on the transmission shaft 3. The bearing 6 includes a bearing outer ring 602 and a bearing inner ring 601 connected to the bearing outer ring 602. One end of the bearing outer ring 602 abuts against the gasket 23, and the other end of the bearing outer ring 602 abuts against the snap ring 12. The snap spring 11 abuts against one end of the bearing inner ring 601 away from the gasket 23.

[0203] The bearing 6 includes a bearing inner ring 601 and a bearing outer ring 602. The bearing inner ring 601 is fastened to the transmission shaft 3 so that the bearing 6 is fixed relative to the transmission shaft 3 in the axial direction of the transmission shaft 3. The bearing outer ring 602 is limited between the gasket 23 and the retaining ring 12, and the gasket 23 abuts against the limiting surface 111 of the installation cavity 102. The retaining ring 12 is interference-fitted with the installation cavity 102. In this way, the movement of the transmission shaft 3 relative to the pump housing 1 along its own axial direction can be limited. Since the transmission shaft 3 is connected to the active rotor 201, the possibility of axial movement of the active rotor 201 can be reduced, thereby avoiding the problem of increased friction between the active rotor 201 and the pump housing 1 due to the axial movement of the active rotor 201. In addition, by providing the retaining ring 11, the axial stability between the transmission shaft 3 and the bearing 6 can be further guaranteed, and the close fit between the bearing inner ring 601 and the transmission shaft 3 can be prevented from loosening and causing the transmission shaft 3 to move relative to the bearing 6.

[0204] In other embodiments, Fig.19 As shown, the pump housing 1 also has an installation cavity 102, the output shaft 501 and the constraint structure 13 are both located in the installation cavity 102, a portion of the transmission shaft 3 is located in the installation cavity 102, and another portion of the transmission shaft 3 extends into the accommodating cavity 101. The constraint structure 13 is a bearing 6, the bearing 6 is located in the installation cavity 102, and the outer wall surface of the bearing 6 contacts the wall surface of the installation cavity 102.

[0205] In this embodiment, the constraint structure 13 is a bearing 6 sleeved on the output shaft 501 and the transmission shaft 3. The bearing 6 is used as the constraint structure 13, which can not only keep the axis of the output shaft 501 and the axis of the transmission shaft 3 in the same line, but also the outer wall surface of the bearing 6 contacts the wall surface of the installation cavity 102, and can also improve the centering accuracy of the transmission shaft 3 relative to the installation cavity 102, thereby further improving the position accuracy of the transmission shaft 3. In this embodiment, since the bearing 6 is used to improve the centering accuracy of the transmission shaft 3 and is also used as the constraint structure 13, this arrangement can reduce the number of components, thereby facilitating the reduction of the overall size of the spherical rotor pump 100 along the axial direction of the transmission shaft 3.

[0206] Furthermore, if Fig.19 As shown, the driving device 5 further includes a main body 502, and the output shaft 501 is connected to the main body 502. A limited surface 111 is formed in the installation cavity 102, and the spherical rotor pump 100 further includes a support block 9, which is located in the installation cavity 102 and abuts against the main body 502, and the bearing 6 is limited between the limited surface 111 and the support block 9.

[0207] In this embodiment, the bearing 6 is tightly sleeved on the transmission shaft 3. At the same time, the bearing 6 is restricted between the limiting surface 111 of the mounting cavity 102 and the support block 9, thereby limiting the movement of the transmission shaft 3 relative to the pump housing 1 along its own axial direction. Since the transmission shaft 3 is connected to the active rotor 201, the possibility of axial movement of the active rotor 201 can be reduced, thereby avoiding the problem of increased friction between the active rotor 201 and the pump housing 1 due to the axial movement of the active rotor 201.

[0208] In some embodiments, Fig. 20 , Fig.21 and Fig. 22 As shown, the output shaft 501 includes a first matching portion 5011, the first matching portion 5011 is provided with a first contact surface 5012, the transmission shaft 3 includes a second matching portion 301, the second matching portion 301 is provided with a second contact surface 3011, and the first contact surface 5012 and the second contact surface 3011 are closely abutted against each other, so that torque can be transmitted between the output shaft 501 and the transmission 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 portion 5011 and the second contact surface 3011 of the second matching portion 301 are closely abutted against each other, and in this way, the transmission connection between the output shaft 501 and the transmission shaft 3 can be realized, and this method has a simple structure and is easy to process and realize.

[0209] Furthermore, the first contact surface 5012 and the second contact surface 3011 are both planes, so that the first contact surface 5012 and the second contact surface 3011 can better fit each other, thereby preventing the output shaft 501 and the transmission shaft 3 from shaking or vibrating during the transmission process.

[0210] Furthermore, the cross-sectional shape of the first matching portion 5011 is a first semicircle, the cross-sectional shape of the second matching 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 matching portion 5011 and the second contact surface 3011 of the second matching portion 301 are tightly against each other, the first matching portion 5011 and the second matching portion 301 can be assembled 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.

[0211] In some other embodiments, the output shaft 501 includes a third matching portion, the transmission shaft 3 includes a fourth matching portion, one of the third matching portion and the fourth matching portion is a prismatic structure, the other of the third matching portion and the fourth matching 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 matches the inner cavity. In this embodiment, the output shaft 501 and the transmission shaft 3 adopt a mode of matching the prismatic structure and the inner cavity, and the shape of the inner cavity matches the prismatic structure. For example, when the prismatic structure is a quadrangular prism, the cross-sectional shape of the inner cavity is a quadrilateral, and when the prismatic structure is a hexagonal prism, the cross-sectional shape of the inner cavity is a hexagon. Such a configuration enables torque to be transmitted between the output shaft 501 and the transmission shaft 3, so that the output shaft 501 can drive the transmission shaft 3 to rotate. In addition, this method can make the output shaft 501 and the transmission shaft 3 more uniformly stressed during the transmission process.

[0212] Further, the prism structure is a regular prism, and the number of the sides of the regular prism is greater than or equal to 3 and less than or equal to 6. The prism structure is a regular prism, which is conducive to further improving the force uniformity of the output shaft 501 and the transmission shaft 3 during the transmission process, thereby facilitating the extension of the service life of the output shaft 501 and the transmission shaft 3. In addition, the number of the sides of the regular prism is 3 to 6, which makes the prism structure easy to process and manufacture, and is also conducive to improving the processing accuracy of the prism structure.

[0213] In some other embodiments, such as Fig.23 , Fig.24 and Fig.25 As shown, one of the output shaft 501 and the transmission shaft 3 is provided with a slot 302, and the other of the output shaft 501 and the transmission shaft 3 is provided with a flat shaft portion 5013, and the flat shaft portion 5013 cooperates with the slot 302 so that torque can be transmitted between the output shaft 501 and the transmission shaft 3. In this embodiment, torque can be transmitted between the output shaft 501 and the transmission shaft 3 through the cooperation between the flat shaft portion 5013 and the slot 302. In addition, this method can make the output shaft 501 and the transmission shaft 3 bear force more evenly during the transmission process.

[0214] Furthermore, one of the output shaft 501 and the transmission 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 transmission shaft 3 is further provided with a mounting portion 5014 connected to the flat shaft portion 5013, and the mounting portion 5014 is interference-fitted with the mounting hole 303. Through the interference fit between the mounting portion 5014 and the mounting hole 303, the output shaft 501 and the transmission shaft 3 are relatively fixed in the axial direction, which is also conducive to preventing the transmission shaft 3 from moving in the axial direction, thereby reducing the possibility of axial movement of the active rotor 201, and further avoiding the problem of increased friction between the active rotor 201 and the pump housing 1 due to the axial movement of the active rotor 201.

[0215] In some embodiments, Figure 3 , Fig.26 As shown, the spherical rotor pump 100 also 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 jointly define an accommodating chamber 101, the rotor assembly 2 is located in the accommodating chamber 101, and the seal 16 is located between the first housing 107 and the second housing 108 and is arranged around the accommodating chamber 101. Among them, a groove 121 is provided on one of the first housing 107 and the second housing 108, and 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 the end surface 1221 of the protrusion 122 abuts against the seal 16 to press the seal 16 into the groove 121.

[0216] In the embodiment of the present application, the pump housing 1 includes a first housing 107 and a second housing 108 connected to each other, and a sealing member 16 is disposed between the first housing 107 and the second housing 108 and is disposed around the accommodating chamber 101, thereby forming a seal between the first housing 107 and the second housing 108, thereby reducing the risk of liquid leakage in the accommodating chamber 101. In addition, a groove 121 and a protrusion 122 are further disposed at the contact portion between 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 compressed state, thereby improving the sealing effect of the sealing member 16, thereby further reducing the risk of liquid leakage.

[0217] In some embodiments, Fig.26 , Fig. 27 and Fig.28 As shown, the thickness h of the protrusion 122 gradually decreases in a direction away from the rotor assembly 2 .

[0218] Taking the groove 121 provided on the first shell 107 and the protrusion 122 provided on the second shell 108 as an example, when the first shell 107 and the second shell 108 are assembled, the protrusion 122 on the second shell 108 squeezes the seal 16. Since the thickness h of the protrusion 122 gradually decreases in the direction away from the rotor assembly 2, the protrusion 122 squeezes the seal 16 and expands the seal 16 radially outward, so that the first shell 107 is subjected to the force from the seal 16. Under the action of the force, the first shell 107 is slightly deformed outward. In this way, after the first shell 107 and the second shell 108 are assembled, it is helpful to avoid the friction force of the rotor assembly 2 when the rotor assembly 2 rotates due to the squeezing between the first shell 107 and the rotor assembly 2.

[0219] Taking the groove 121 provided on the second housing 108 and the protrusion 122 provided on the first housing 107 as an example, when the first housing 107 and the second housing 108 are assembled, the protrusion 122 on the first housing 107 squeezes the seal 16. Since the thickness h of the protrusion 122 gradually decreases in the direction away from the rotor assembly 2, the protrusion 122 squeezes the seal 16 and expands the seal 16 radially outward, so that the second housing 108 is subjected to the force from the seal 16. Under the action of the force, the second housing 108 produces a slight outward deformation. In this way, after the first housing 107 and the second housing 108 are assembled, it is helpful to avoid the squeezing between the second housing 108 and the rotor assembly 2, which causes the friction force to increase when the rotor assembly 2 rotates.

[0220] In some embodiments, Fig.28 and Fig.29 As shown, the protrusion 122 is an annular structure, so that any position of the seal 16 can be squeezed by the protrusion 122. In addition, the cross-sectional shape of the protrusion 122 can be configured as a trapezoid, wherein the short bottom side of the trapezoid corresponds to the surface of the seal 16 away from the rotor assembly 2, and the long bottom side of the trapezoid corresponds to the surface of the seal 16 close to the rotor assembly 2. Thus, a shape in which the thickness h of the protrusion 122 gradually decreases along the direction away from the rotor assembly 2 can be configured.

[0221] In some embodiments, as shown in Figure 27, the active rotor 201 has a first axis a, and the active rotor 201 can rotate around the first axis a relative to the pump housing 1; the driven rotor 202 has a second axis b, and the driven rotor 202 can rotate around the second axis b relative to the pump housing 1, and the first axis a intersects with the second axis b.

[0222] In one embodiment, the end surface 1221 of the protrusion 122 is perpendicular to the second axis b. At this time, the thickness h of the protrusion 122 does not change along the direction away from the rotor assembly 2, that is, the protrusion 122 has a uniform thickness h. In this case, after the first shell 107 and the second shell 108 are assembled, it can at least ensure that the shell where the groove 121 is located will not be slightly deformed outward or inward, thereby avoiding the shell where the groove 121 is located being squeezed with the rotor assembly 2 after assembly.

[0223] In another embodiment, Fig. 27As shown, the angle β between the end face 1221 of the protrusion 122 and the second axis b is greater than 90° and less than or equal to 135°. The angle β between the end face 1221 of the protrusion 122 and the second axis b is greater than 90°. At this time, the thickness h of the protrusion 122 gradually decreases in the direction away from the rotor assembly 2. In this case, when the first shell 107 and the second shell 108 are assembled, the shell where the groove 121 is located will produce a slight deformation outward. In this way, after the first shell 107 and the second shell 108 are assembled, it is helpful to avoid the extrusion between the shell where the groove 121 is located and the rotor assembly 2, which causes the friction force to increase when the rotor assembly 2 rotates.

[0224] In some embodiments, Fig.26 As shown, the groove 121 includes a first portion 1211 and a second portion 1212 which are connected to each other, the second portion 1212 is located on a side of the first portion 1211 away from the protrusion 122, wherein the width of the first portion 1211 is greater than the width of the second portion 1212, the protrusion 122 is located in the first portion 1211, and the sealing member 16 is located at least in the second portion 1212. In this way, during the assembly of the first shell 107 and the second shell 108, the sealing member 16 enters the second portion 1212 with a smaller width from the first portion 1211 with a larger width under the squeezing 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, thereby further improving the sealing effect of the sealing member 16, thereby further reducing the risk of liquid leakage.

[0225] In some embodiments, Fig. 27 and Fig.30 As shown, the first shell 107 and the second shell 108 both include a shell body 131 and a docking portion 132, the shell body 131 has an open end, and the docking portion 132 is located outside the shell body 131 and is arranged around the open end. The docking portion 132 of the first shell 107 and the docking portion 132 of the second shell 108 are connected by fasteners, and the groove 121 and the protrusion 122 are both arranged at the docking portion 132. By arranging the docking portion 132 around the shell body 131 and connecting the docking portion 132 of the first shell 107 and the second shell 108 by fasteners, the contact area between the first shell 107 and the second shell 108 can be increased, thereby improving the sealing performance of the pump shell 1 and the connection stability between the first shell 107 and the second shell 108.

[0226] In some embodiments, Fig.29 , Fig.30As shown, the docking portion 132 of the first shell 107 and / or the docking portion 132 of the second shell 108 is provided with a reinforcing rib 133. During the operation of the spherical rotor pump 100, the first shell 107 and the second shell 108 will be subjected to the pressure of the liquid in the volume-changing chamber 203, and the pressure causes the first shell 107 and the second shell 108 to have a movement tendency away from each other. The pressure is relatively large, so that the connection portion of the first shell 107 and the second shell 108 is easily deformed. In this embodiment, the docking portion 132 of the first shell 107 and / or the second shell 108 is provided with a reinforcing rib 133. By providing the reinforcing rib 133, the structural strength and structural rigidity of the docking portion 132 can be improved, so that the docking portion 132 is not easily deformed, which is conducive to improving the connection stability between the first shell 107 and the second shell 108.

[0227] In some embodiments, Fig. 27 As shown, the distance L1 from the groove 121 to the wall of the accommodating cavity 101 is greater than or equal to 0.8 mm, which is conducive to making the structure between the groove 121 and the accommodating cavity 101 have better structural strength and structural rigidity and is not prone to damage or deformation.

[0228] In some embodiments, Fig.28 As shown, the distance L2 from the groove 121 to the outer surface of the docking portion 132 is greater than or equal to 0.8 mm, which is conducive to making the structure between the groove 121 and the outer surface of the docking portion 132 have better structural strength and structural rigidity and is not prone to damage or deformation.

[0229] In some embodiments, Fig.28 As shown, the distance L3 from the bottom of the groove 121 to the surface of the docking part 132 along the thickness direction is greater than or equal to 0.8 mm. This is conducive to making the structure between the bottom of the groove 121 and the surface of the docking part 132 along the thickness direction have better structural strength and structural rigidity, and is not easy to be damaged or deformed.

[0230] In some embodiments, Fig.28 As shown, the width w of the protrusion 122 is greater than or equal to 0.8 mm, which is conducive to making the protrusion 122 have better structural strength and structural rigidity and is not easy to be damaged or deformed.

[0231] In some embodiments, the distance L2 from the groove 121 to the outer surface of the docking portion 132 is greater than the distance L1 from the groove 121 to the wall of the accommodating chamber 101. In this way, the groove 121 is arranged at a position farther from the outer surface of the docking portion 132, but closer to the accommodating chamber 101. Since the seal 16 is arranged in the groove 121, it is possible to prevent more liquid from entering the gap between the two docking portions 132. In addition, when the groove 121 is arranged closer to the accommodating chamber 101, it is beneficial to shorten the arm of the torque formed by the pressure of the liquid in the variable cavity 203, thereby being more conducive to improving the connection stability between the first shell 107 and the second shell 108.

[0232] In some embodiments, Fig.29 As shown, the seal 16 is an annular seal 16, so that the seal 16 can be arranged around the accommodating cavity 101, thereby forming a closed sealing structure between the first shell 107 and the second shell 108. In addition, the cross-sectional shape of the seal 16 is circular, so that the seal 16 has a relatively obvious deformation under the extrusion of the protrusion 122, so that the space in the groove 121 can be relatively fully filled and closely contacted with the wall surface of the groove 121, so as to obtain a better sealing performance.

[0233] In some embodiments, Fig.12 , Fig.31 , Fig.32 , Fig.33 as well as Fig.34 As shown, the driven rotor 202 has a second axis b, and the driven rotor 202 can rotate around the second axis b relative to the pump housing 1, and the active rotor 201 has a first axis a, and the active rotor 201 can rotate around the first axis a relative to the pump housing 1. The driven rotor 202 includes a base 214 and a pin shaft portion 209 arranged on the base 214, and the active rotor 201 is provided with a groove 210, and the pin shaft portion 209 is restricted in the groove 210 and can rotate around the third axis c relative 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 the central angle is less than or equal to 180°, and the minimum distance between the two side surfaces 2092 is equal to the chord length d of the first mating surface 2091.

[0234] In this embodiment, 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, wherein the first mating surface 2091 is an arcuate surface, and the first mating surface 2091 is used to cooperate with the groove 210, so that the pin shaft portion 209 is restricted in the groove 210 and can rotate around the third axis c relative to the groove 210. Since the first mating surface 2091 is an arcuate surface and the central angle is less than or equal to 180°, the first mating surface 2091 will not have a tendency to shrink inwards at positions close to both sides. In addition, the minimum distance between the two side surfaces 2092 located on both sides of the first mating surface 2091 is equal to the chord length d of the first mating surface 2091, which makes the two side surfaces 2092 also have no tendency to shrink inwards. In this way, the formation of undercuts between the side of the pin shaft portion 209 and the base 214 can be avoided, thereby reducing the possibility of interference between the rotor where the groove 210 is located and the pin shaft portion 209 or the base 214 when the pin shaft portion 209 and the groove 210 rotate in cooperation, thereby reducing the problem of wear caused by interference.

[0235] In some embodiments, please refer to Fig.34 , both side surfaces 2092 are planes, and the two side surfaces 2092 are arranged parallel to each other. When the side surfaces 2092 are planes, it is advantageous to make the volume of the variable volume cavity 203 formed larger, thereby increasing the volume of liquid pumped in a single time. In addition, when the two side surfaces 2092 are parallel to each other, the distance between the two side surfaces 2092 at any position only needs to be equal to the chord length of the first mating surface 2091, so that the distance between the two side surfaces 2092 can meet the setting requirements.

[0236] In some other embodiments, the two side surfaces 2092 may also be curved surfaces. In this case, it is necessary to obtain the position where the distance between the two side surfaces 2092 is the smallest, and 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 .

[0237] In some other embodiments, both side surfaces 2092 are planes, and the angle between the spatial plane where one of the side surfaces 2092 is located and the spatial plane where the other side surface 2092 is located is greater than 0° and less than or equal to 15°. In this embodiment, the angle between the spatial plane where one of the side surfaces 2092 is located and the spatial plane where the other side surface 2092 is located is α. When α is greater than 0°, the two side surfaces 2092 are not parallel to each other, but show a tendency to expand outward, and at this time, the formation of an undercut between the side of the pin shaft portion 209 and the base 214 can also be avoided. However, α should not be too large, otherwise it will cause the volume of the variable cavity 203 to be reduced. Therefore, in this embodiment, α is limited to the range of 0° to 15° to reduce the impact on the volume of the variable cavity 203.

[0238] In some embodiments, Fig.31 , Fig.35 As shown, the groove 210 has a second mating surface 2101 and a clearance portion 2102 located on both sides of the second mating surface 2101, the second mating surface 2101 is an arcuate surface, the second mating surface 2101 is used to match with the first mating surface 2091, and there is a gap between the clearance portion 2102 and the pin shaft portion 209. In this embodiment, the groove 210 has a second mating surface 2101, and the second mating surface 2101 is an arcuate surface, so that it can better match with the first mating surface 2091 of the pin shaft portion 209. In addition, the groove 210 also has a clearance portion 2102 located on both sides of the second mating surface 2101, and there is a gap between the clearance portion 2102 and the pin shaft portion 209. In the process of the pin shaft and the groove 210 rotating in coordination, the clearance portion 2102 is used to avoid position, so as to prevent the edge position of the groove 210 from interfering with the pin shaft portion 209 and causing wear.

[0239] Furthermore, the gap between the clearance portion 2102 and the pin shaft portion 209 gradually decreases in the direction close to the second mating surface 2101. This arrangement is conducive to making the surface of the groove 210 smoother and preventing a sudden change at the location of the clearance portion 2102.

[0240] Furthermore, the gap between the avoidance portion 2102 and the pin shaft portion 209 is greater than or equal to 0.05 mm and less than or equal to 0.6 mm. If the gap size between the avoidance portion 2102 and the pin shaft portion 209 is too small, the effect of the avoidance portion 2102 in preventing wear will become less obvious; on the contrary, if the gap size between the avoidance portion 2102 and the pin shaft portion 209 is too large, particulate impurities are easily introduced between the groove 210 and the pin shaft portion 209, which will also lead to aggravated wear between the driven rotor 202 and the active rotor 201, and even problems such as jamming and damage may occur. In this embodiment, the gap between the avoidance portion 2102 and the pin shaft portion 209 is set to a range of 0.05 mm to 0.6 mm, which can not only make the avoidance portion 2102 better play the effect of preventing wear, but also better avoid the situation where particulate impurities are easily introduced between the groove 210 and the pin shaft portion 209.

[0241] In some embodiments, Fig.33 , Fig.35As shown, the base 214 has two first plane portions 2141 facing the active rotor 201, and the two first plane portions 2141 are located on both sides of the pin shaft portion 209. The active rotor 201 has two second plane portions 2021 facing the base 214, and the two second plane portions 2021 are arranged one by one opposite to the two first plane portions 2141. The pin shaft portion 209, the wall surface of the accommodating cavity 101, the first plane portion 2141 and the corresponding second plane portion 2021 jointly define the variable cavity 203. When the pin shaft portion 209 rotates around the third axis relative to the groove 210, the volume of the variable cavity 203 changes.

[0242] In this embodiment, the surface of the base 214 facing the active rotor 201 is formed into two first plane portions 2141, and the surface of the active rotor 201 facing the driven rotor 202 is formed into two second plane portions 2021. On this basis, the pin shaft portion 209, the wall surface of the accommodating cavity 101, the first plane portion 2141 and the second plane portion 2021 jointly define the variable cavity 203. Compared with the curved surface, the plane portion is easier to process and can also obtain higher processing accuracy, which is conducive to controlling the volume of the variable cavity 203.

[0243] In some embodiments, Fig.31 As shown, the end of the avoidance portion 2102 away from the second mating surface 2101 is the first end 2103, the end of the avoidance portion 2102 close to the second mating portion is the second end 2104, the line connecting the first end 2103 and the third axis is the first line, the line connecting the second end 2104 and the third axis is the second line, and a first angle γ is formed between the first line and the second line; the end of the side surface 2092 away from the first mating surface 2091 is the third end 2093, the end of the side surface 2092 close to the first mating surface 2091 is the fourth end 2094, the line connecting the third end 2093 and the third axis is the third line, the line connecting the fourth end 2094 and the third axis is the fourth line, and a second angle θ is formed between the third line and the fourth line, wherein the first angle γ is greater than the second angle θ.

[0244] Such arrangement enables the extension length of the avoidance portion 2102 along the circumferential direction to be greater than the extension length of the side surface 2092 along the circumferential direction. This ensures that during the coordinated rotation of the pin shaft portion 209 and the groove 210, the avoidance portion 2102 can always effectively play a avoiding role to prevent interference and wear between the edge position of the groove 210 and the pin shaft portion 209.

[0245] Furthermore, the second angle is less than 40°. If the second angle is too large, then the first angle will be too large accordingly, which will cause the clearance portion 2102 to occupy too large an area in the groove 210, while the second mating surface 2101 to occupy too small an area in the groove 210, thereby affecting the mating stability between the pin shaft portion 209 and the groove 210, making it easy for the rotor assembly 2 to vibrate and cause noise when rotating.

[0246] In some embodiments, the spherical rotor pump 100 has a first state, in which the volume of one of the two variable-volume cavities 203 reaches a minimum value, and the volume of the other of the two variable-volume cavities 203 reaches a maximum value. In the first state, the first plane portion 2141 and the corresponding second plane portion 2021 in any variable-volume cavity 203 maintain a distance. This arrangement makes the minimum volume of the variable-volume cavity 203 greater than 0, that is, during the rotation of the rotor assembly 2, the volume of the variable-volume cavity 203 is always greater than 0, that is, the first plane portion 2141 and the second plane portion 2021 will never contact each other, so that the first plane portion 2141 and the second plane portion 2021 can be prevented from adhering to each other, and the spherical rotor pump 100 can be prevented from not being able to work normally due to the adhesion of the two.

[0247] In some embodiments, Fig.35 As shown, a transition chamfer 2105 is formed between the clearance portion 2102 and the second plane portion 2021. This arrangement allows a relatively gentle transition to be formed between the edge of the groove 210 and the second plane portion 2021, thereby reducing the possibility of interference and wear between the connection portion between the groove 210 and the second plane portion 2021 and the pin shaft portion 209.

[0248] In some embodiments, the first mating surface 2091 and the second mating surface 2101 are made of materials with the same expansion coefficient. During the rotation of the rotor assembly 2, heat will be generated due to friction between the first mating surface 2091 of the pin shaft portion 209 and the second mating surface 2101 of the groove 210. Under the influence of thermal expansion and contraction, the structure of the driven rotor 202 at the first mating surface 2091 and the structure of the active rotor 201 at the second mating surface 2101 will expand. The first mating surface 2091 and the second mating surface 2101 are made of materials with the same expansion coefficient, so that the expansion degree of the two can be kept consistent. In this way, the first mating surface 2091 and the second mating surface 2101 can always maintain a good matching relationship, preventing the phenomenon of motion jamming caused by poor matching.

[0249] Furthermore, 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 must have the same expansion coefficient 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.

[0250] In some embodiments, Fig.33 As shown, the base 214 also has an outer surface 2142 for matching with the wall surface of the accommodating chamber 101, and the outer surface 2142 is a spherical surface. Therefore, it is beneficial for the driven rotor 202 to rotate relatively smoothly relative to the pump housing 1. In addition, the end surfaces 2095 at both ends of the pin shaft portion 209 along the third axis direction are spherical surfaces consistent with the outer surface 2142, so that the end surfaces 2095 at both ends of the pin shaft portion 209 can be guaranteed to have good sealing performance with the pump housing 1, thereby ensuring the sealing performance of the variable cavity 203.

[0251] The second aspect of the present application provides a tooth cleaning device 1000, which includes the spherical rotor pump 100 in any of the above embodiments. Fig.36 As shown, the tooth cleaning device 1000 may include a body 200 , a nozzle 300 disposed on the body 200 , and a spherical rotor pump 100 for delivering liquid to the nozzle 300 .

[0252] In the tooth cleaning device 1000 in the embodiment of the present application, the housing of the spherical rotor pump 100 has a receiving chamber 101 and a mounting chamber 102, the receiving chamber 101 and the mounting chamber 102 are separated by a partition 103, the rotor assembly 2 is located in the receiving chamber 101, and the transmission shaft 3 passes through a through hole 104 on the partition 103 to connect with the active rotor 201 in the receiving chamber 101. The spherical rotor pump 100 is also provided with a sealing ring 4, which is used to seal the gap between the transmission shaft 3 and the hole wall of the through hole 104, or to seal the gap between the transmission shaft 3 and the inner wall of the mounting chamber 102. In this way, even if the gap sealing failure occurs between the rotor assembly 2 and the inner wall of the receiving chamber 101, the risk of liquid overflowing from the transmission shaft 3 can be reduced.

[0253] The above contents are only specific implementation methods of the present application, but the protection scope of the present application is not limited thereto. Any technician familiar with the technical field can easily think of changes or substitutions within the technical scope disclosed in the present application, which should be included in the protection scope of the present application. Therefore, the protection scope of the present application should be based on the protection scope of the claims.

Claims

1. A spherical rotor pump, characterized in that: include: A pump housing, wherein the pump housing has a receiving cavity and a mounting cavity, wherein the receiving cavity and the mounting cavity are separated by a partition, and the partition is provided with a through hole; A rotor assembly, wherein the rotor assembly comprises an active rotor and a driven rotor, wherein the active rotor and the driven rotor are both located in the accommodating cavity, wherein the active rotor, the driven rotor and the wall surface of the accommodating cavity jointly define a variable capacity cavity, wherein the active rotor can drive the driven rotor to rotate, and when the active rotor drives the driven rotor to rotate, the volume of the variable capacity cavity changes; a transmission shaft, wherein the transmission shaft passes through the through hole, a portion of the transmission shaft is located in the mounting cavity, and another portion of the transmission shaft extends into the accommodating cavity and is connected to the active rotor; and A sealing ring, the sealing ring is used to seal the gap between the transmission shaft and the hole wall of the through hole, or to seal the gap between the transmission shaft and the inner wall of the installation cavity; The driven rotor comprises a base and a pin portion arranged on the base, the driving rotor is provided with a groove, the pin portion is restricted in the groove and can rotate relative to the groove around a third axis; The pin shaft portion has a first mating surface and side surfaces located on both sides of the first mating surface, the first mating surface connects the two side surfaces, the first mating surface is an arc surface and the central angle of the first mating surface is less than or equal to 180°, and the minimum distance between the two side surfaces is equal to the chord length of the first mating surface.

2. The spherical rotor pump according to claim 1, characterized in that: The sealing ring is arranged in the installation cavity, and the sealing ring is sleeved on the transmission shaft and abuts against the partition.

3. The spherical rotor pump according to claim 2, characterized in that: The spherical rotor pump also includes: A bearing, wherein the bearing is located in the installation cavity, the bearing is sleeved on the transmission shaft, the bearing is arranged on a side of the sealing ring away from the partition, and the bearing is in contact with a wall surface of the installation cavity; and A spacer is located between the bearing and the sealing ring.

4. The spherical rotor pump according to claim 3, characterized in that: The installation cavity comprises a first section and a second section which are communicated with each other, wherein the second section is located at a side of the first section away from the partition; The cross-sectional area of ​​the second section is greater than that of the first section, so that a step-shaped limiting surface is formed at the connection position between the second section and the first section, the sealing ring is located in the first section, the bearing and the isolation member are both located in the second section, and the isolation member is against the limiting surface.

5. The spherical rotor pump according to claim 4, characterized in that: The isolating member is tightly 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 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. The spherical rotor pump according to claim 3, characterized in that: The bearing comprises a bearing inner ring and a bearing outer ring connected to the bearing inner ring, and the bearing inner ring is tightly sleeved on the transmission shaft; The isolating member is an annular gasket, the inner diameter of which is greater than the outer diameter of the bearing inner ring, so that the gasket and the bearing inner ring are spaced apart in the radial direction.

7. The spherical rotor pump according to claim 3, characterized in that: The bearing comprises a bearing inner ring and a bearing outer ring connected to the bearing inner ring, and the bearing inner ring is tightly sleeved on the transmission shaft; The isolating member is an annular gasket, the inner diameter of which is smaller than the outer diameter of the inner ring of the bearing. A relief notch is formed on the side of the gasket close to the bearing, and the relief notch is arranged opposite to the inner ring of the bearing to avoid the inner ring of the bearing.

8. The spherical rotor pump according to claim 1, characterized in that: The sealing ring is arranged in the accommodating cavity, and the sealing ring is sleeved on the transmission shaft and abuts against the partition.

9. The spherical rotor pump according to claim 8, characterized in that: A first placement groove is arranged in the accommodating cavity, and the sealing ring is located in the first placement groove.

10. The spherical rotor pump according to claim 9, characterized in that: The spherical rotor pump further comprises an anti-wear gasket, which is arranged between the active rotor and the sealing ring.

11. The spherical rotor pump according to claim 10, characterized in that: A second placement groove is also provided in the accommodating cavity. The second placement groove is communicated with the first placement groove. Part of the structure of the anti-wear gasket is located in the second placement groove. The radial dimension of the first placement groove is smaller than the radial dimension of the second placement groove.

12. The spherical rotor pump according to claim 11, characterized in that The thickness of the anti-wear pad is greater than the depth of the second placement groove, so that a part of the structure of the anti-wear pad extends out of the second placement groove.

13. The spherical rotor pump according to claim 11, characterized in that: The rotor assembly comprises a driving rotor and a driven rotor, both of which are located in the accommodating cavity, and the transmission shaft is connected to the driving rotor; A limiting end surface is arranged at one end of the active rotor close to the anti-wear pad, the limiting end surface is a plane, and the limiting end surface abuts against the anti-wear pad.

14. The spherical rotor pump according to claim 13, characterized in that A limiting portion is formed at one end of the active rotor away from the driven rotor, and the limiting end surface is formed on the limiting portion; A third placement groove is also provided in the accommodating cavity. The third placement groove is communicated with the second placement groove. The limiting portion is located in the third placement groove. The radial dimension of the second placement groove is smaller than the radial dimension of the third placement groove.

15. The spherical rotor pump according to claim 11, characterized in that The anti-wear gasket is tightly 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 compressed, the dimension of the sealing ring along the axial direction of the transmission shaft is larger than the dimension of the first seating groove along the axial direction of the transmission shaft.

16. The spherical rotor pump according to claim 1, characterized in that The sealing ring is a Y-shaped sealing ring, which includes a sealing ring body. An inner lip and an outer lip are arranged on one side of the sealing ring body, and the inner lip and the outer lip are against the partition.

17. The spherical rotor pump according to claim 1, characterized in that: The pump housing comprises a first shell and a second shell, the first shell and the second shell are connected, the first shell and the second shell together define the accommodating cavity, and the second shell defines the installation cavity; The spherical rotor pump further includes a driving device, the driving device including a main body and an output shaft connected to the main body, the main body is connected to the second housing, the output shaft is located in the mounting cavity and connected to the transmission shaft; The spherical rotor pump further comprises a bearing, the bearing is located in the installation cavity, the bearing is sleeved on the transmission shaft and / or the output shaft, the bearing is arranged on a side of the sealing ring away from the partition, and the bearing is in contact with the wall surface of the installation cavity; The spherical rotor pump further comprises a support block, which is arranged on a side of the bearing away from the partition plate, and the support block is fixed in the installation cavity.

18. The spherical rotor pump according to claim 17, characterized in that The main body has an end face arranged toward the pump housing, the end face is formed with a protruding structure, the protruding structure is located in the installation cavity, the support block abuts against the protruding structure; the radial dimension of the support block is greater than the radial dimension of the protruding structure.

19. The spherical rotor pump according to claim 1, characterized in that: The active rotor comprises a first support member and a first encapsulated body, wherein the first support member is encapsulated inside the first encapsulated body to serve as an inner skeleton of the active rotor, and the transmission shaft extends into the first encapsulated body and is connected to the first support member, wherein the transmission shaft is fixedly connected to the first support member, or the transmission shaft and the first support member are an integrated structure; And / or, the driven rotor includes a second support member and a second encapsulation body, and the second encapsulation body covers at least a portion of the second support member.

20. The spherical rotor pump according to claim 1, characterized in that The spherical rotor pump further comprises a limiting structure, which is arranged between the transmission shaft and the pump housing, and is used to limit the movement of the transmission shaft relative to the pump housing along its own axial direction.

21. The spherical rotor pump according to claim 20, characterized in that The pump housing forms a finite surface; The limiting structure includes a first component, a second component and a gasket. The first component is connected to the transmission shaft so that the first component is fixed relative to the transmission shaft along the axial direction of the transmission shaft. The second component is fixedly connected to the pump housing. The gasket abuts against the limiting surface, and the first component is limited between the gasket and the second component.

22. The spherical rotor pump according to claim 21, characterized in that The first component is a bearing sleeved on the transmission shaft; The bearing comprises a bearing outer ring and a bearing inner ring connected to the bearing outer ring, the bearing inner ring is fastened to the transmission shaft, one end of the bearing outer ring abuts against the gasket, and the other end of the bearing outer ring abuts against the second component.

23. The spherical rotor pump according to claim 22, characterized in that The limiting structure further includes a third component, the third component is fixedly connected to the transmission shaft, and the third component abuts against an end of the bearing inner ring away from the gasket.

24. The spherical rotor pump according to claim 23, characterized in that The third component is a retaining spring sleeved on the transmission shaft or a pin fixedly installed on the transmission shaft.

25. The spherical rotor pump according to claim 21, characterized in that The first component is a retaining spring sleeved on the transmission shaft, or the first component is a pin fixedly mounted on the transmission shaft.

26. The spherical rotor pump according to claim 21, characterized in that The second component is a snap ring, and the snap ring is interference fit with the installation cavity.

27. The spherical rotor pump according to claim 20, characterized in that The driving rotor and the driven rotor are connected via a pin shaft.

28. The spherical rotor pump according to claim 27, characterized in that The active rotor comprises a first support member and a first encapsulated body, a part of the structure of the first support member is encapsulated inside the first encapsulated body to serve as an inner skeleton of the active rotor, and another part of the structure of the first support member is located outside the first encapsulated body to form a connecting portion; The driven rotor includes a second support member and a second encapsulated body, the second encapsulated body covers at least a portion of the second support member, a through groove is provided on the second encapsulated body, the connecting portion extends into the interior of the second encapsulated body through the through groove, and is connected to the second support member through the pin shaft.

29. The spherical rotor pump according to claim 28, characterized in that The width of the through slot is greater than the width of the connecting portion, so that there is a distance between the connecting portion and the side wall of the through slot.

30. The spherical rotor pump according to claim 27, characterized in that The driving rotor has a first axis, the driving rotor can rotate relative to the pump housing around the first axis, the driven rotor has a second axis, the driven rotor can rotate relative to the pump housing around the second axis, and the first axis intersects the second axis; The driven rotor is provided with a groove, the active rotor is formed with a pin shaft portion, the surface of the pin shaft portion is a cylindrical surface or a semi-cylindrical surface, the pin shaft portion is confined in the groove and can rotate around a third axis relative to the groove; the center axis of the pin shaft coincides with the third axis.

31. The spherical rotor pump according to claim 1, characterized in that The spherical rotor pump further comprises a driving device and a constraint structure, wherein the driving device has an output shaft, and the output shaft can drive the transmission shaft to rotate; The restraining structure is sleeved on the output shaft and the transmission shaft to keep the output shaft and the transmission shaft fixed.

32. The spherical rotor pump according to claim 31, characterized in that The output shaft and the constraint structure are both located in the installation cavity, a portion of the transmission shaft is located in the installation cavity, and another portion of the transmission shaft extends into the accommodating cavity; The restraining structure is a sleeve, and there is a distance between the outer wall surface of the sleeve and the wall surface of the installation cavity.

33. The spherical rotor pump according to claim 31, characterized in that The output shaft and the constraint structure are both located in the installation cavity, a portion of the transmission shaft is located in the installation cavity, and another portion of the transmission shaft extends into the accommodating cavity; The constraint structure is a bearing, the bearing is located in the installation cavity, and the outer wall surface of the bearing is in contact with the wall surface of the installation cavity.

34. The spherical rotor pump according to claim 33, characterized in that The driving device further comprises a main body, and the output shaft is connected to the main body; A limited surface is formed in the installation cavity. The spherical rotor pump further comprises a support block, which is located in the installation cavity and abuts against the main body. The bearing is confined between the limited surface and the support block.

35. The spherical rotor pump according to claim 31, characterized in that The output shaft includes a first matching portion, which is provided with a first contact surface; the transmission shaft includes a second matching portion, which is provided with a second contact surface; the first contact surface is tightly against the second contact surface so that torque can be transmitted between the output shaft and the transmission shaft.

36. The spherical rotor pump according to claim 35, characterized in that The first contact surface and the second contact surface are both planes.

37. The spherical rotor pump according to claim 35, characterized in that The cross-sectional shape of the first matching portion is a first semicircle, the cross-sectional shape of the second matching portion is a second semicircle, and the radius of the first semicircle is equal to the radius of the second semicircle.

38. The spherical rotor pump according to claim 31, characterized in that The output shaft includes a third matching portion, and the transmission shaft includes a fourth matching portion. One of the third matching portion and the fourth matching portion is a prismatic structure, and the other of the third matching portion and the fourth matching portion is a mounting sleeve. The mounting sleeve has an inner cavity, and the shape of the inner cavity matches the prismatic structure, and the prismatic structure matches the inner cavity.

39. The spherical rotor pump according to claim 31, characterized in that One of the output shaft and the transmission shaft is provided with a slot, and the other of the output shaft and the transmission shaft is provided with a flat shaft portion, and the flat shaft portion cooperates with the slot to enable torque to be transmitted between the output shaft and the transmission shaft.

40. The spherical rotor pump according to claim 39, characterized in that One of the output shaft and the transmission shaft is further provided with a mounting hole extending in the axial direction, and the other of the output shaft and the transmission shaft is further provided with a mounting portion connected to the flat shaft portion, and the mounting portion is interference fit with the mounting hole.

41. The spherical rotor pump according to claim 1, characterized in that The spherical rotor pump also includes a sealing member; The pump housing comprises a first shell and a second shell connected to the first shell, the first shell and the second shell jointly define the accommodating cavity, and the sealing member is located between the first shell and the second shell and is arranged around the accommodating cavity; A groove is provided on one of the first shell and the second shell, and a protrusion is provided on the other of the first shell and the second shell. The protrusion extends into the groove, and the end surface of the protrusion abuts against the sealing member to press the sealing member into the groove.

42. The spherical rotor pump according to claim 41, characterized in that The thickness of the protrusion gradually decreases in a direction away from the rotor assembly.

43. The spherical rotor pump according to claim 42, characterized in that The protrusion is an annular structure, and the cross-sectional shape of the protrusion is a trapezoid.

44. The spherical rotor pump according to claim 41, characterized in that The driving rotor has a first axis, and the driving rotor is rotatable relative to the pump housing about the first axis; The driven rotor has a second axis, the driven rotor can rotate relative to the pump housing about the second axis, and the first axis intersects the second axis; The end face of the protrusion is perpendicular to the second axis, or the 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 spherical rotor pump according to claim 41, characterized in that The groove includes a first part and a second part connected to each other, the second part is located on a side of the first part away from the protrusion, the width of the first part is greater than the width of the second part, the protrusion is located in the first part, and the seal is at least located in the second part.

46. ​​The spherical rotor pump according to claim 41, characterized in that The first shell and the second shell each include a shell body portion and a docking portion, the shell body portion has an open end, and the docking portion is located outside the shell body portion and is arranged around the open end.

47. The spherical rotor pump according to claim 46, characterized in that The docking portion of the first shell and / or the docking portion of the second shell is provided with reinforcing ribs.

48. The spherical rotor pump according to claim 46, characterized in that The distance from the groove to the wall of the accommodating cavity is greater than or equal to 0.8 mm; and / or, the distance from the groove to the outer surface of the docking portion is greater than or equal to 0.8 mm; and / or, the distance from the bottom of the groove to the surface of the butt joint along the thickness direction is greater than or equal to 0.8 mm; And / or, the width of the protrusion is greater than or equal to 0.8 mm.

49. The spherical rotor pump according to claim 46, characterized in that The distance from the groove to the outer surface of the docking portion is greater than the distance from the groove to the wall surface of the accommodating cavity.

50. The spherical rotor pump according to claim 41, characterized in that The sealing member is an annular sealing member, and the cross-sectional shape of the sealing member is circular.

51. The spherical rotor pump according to claim 1, characterized in that The driven rotor has a second axis, and the driven rotor can rotate relative to the pump housing about the second axis; The drive rotor has a first axis about which the drive rotor is rotatable relative to the pump housing.

52. The spherical rotor pump according to claim 51, characterized in that The two side surfaces are both planes, and the two side surfaces are arranged parallel to each other; or, the two side surfaces are both curved surfaces.

53. The spherical rotor pump according to claim 51, characterized in that Both of the side surfaces are planes, and an angle between a spatial plane where one of the side surfaces is located and a spatial plane where the other side surface is located is greater than 0° and less than or equal to 15°.

54. The spherical rotor pump according to claim 51, characterized in that The groove has a second mating surface and avoidance portions located on both sides of the second mating surface, the second mating surface is an arc-shaped surface, the second mating surface is used to match with the first mating surface, and there is a gap between the avoidance portion and the pin shaft portion.

55. The spherical rotor pump according to claim 54, characterized in that Along the direction approaching the second matching surface, the gap between the clearance portion and the pin shaft portion gradually decreases.

56. The spherical rotor pump according to claim 55, characterized in that A gap between the clearance portion and the pin shaft portion is greater than or equal to 0.05 mm and less than or equal to 0.6 mm.

57. The spherical rotor pump according to claim 54, characterized in that The base has two first plane portions facing the active rotor, the two first plane portions are located on both sides of the pin shaft portion, and the active rotor has two second plane portions facing the base, the two second plane portions are arranged opposite to the two first plane portions one by one; The pin shaft portion, the wall surface of the accommodating cavity, the first plane portion and the corresponding second plane portion jointly define a variable cavity. When the pin shaft portion rotates relative to the groove around the third axis, the volume of the variable cavity changes.

58. The spherical rotor pump according to claim 57, characterized in that An end of the air avoidance portion away from the second mating surface is a first end, an end of the air avoidance portion close to 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; An end of the side surface away from the first mating surface is a third end, an end of the side surface close to the first mating surface is a fourth end, a line connecting the third end and the third axis is a third line, a line connecting the fourth end and the third axis is a fourth line, and a second angle is formed between the third line and the fourth line; The first angle is greater than the second angle.

59. The spherical rotor pump according to claim 58, characterized in that The second angle is less than 40°.

60. The spherical rotor pump according to claim 57, characterized in that The spherical rotor pump has a first state, in which the volume of one of the two variable-volume chambers reaches a minimum value, and the volume of the other of the two variable-volume chambers reaches a maximum value; In the first state, the first plane portion and the corresponding second plane portion in any variable cavity maintain a distance.

61. The spherical rotor pump according to claim 57, characterized in that A transition chamfer is formed between the avoidance portion and the second planar portion.

62. The spherical rotor pump according to claim 54, characterized in that The first mating surface and the second mating surface are made of materials with the same expansion coefficient.

63. The spherical rotor pump according to claim 62, characterized in that The first mating surface and the second mating surface are made of the same material.

64. The spherical rotor pump according to claim 51, characterized in that The base also has an outer surface for matching with the wall of the accommodating cavity, and the outer surface is a spherical surface; The end surfaces of both ends of the pin shaft portion along the third axis direction are spherical surfaces consistent with the outer surface.

65. A teeth cleaning device, characterized in that: A spherical rotor pump comprising the spherical rotor pump described in any one of claims 1 to 64.

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