Spherical rotor pump and dental cleaning device

Abstract

A spherical rotor pump and a dental cleaning device. The spherical rotor pump comprises: a pump housing, the pump housing being provided with a containing cavity and a mounting cavity, the containing cavity being separated from the mounting cavity by means of a partition plate, and the partition plate being provided with a through hole; a rotor assembly, the rotor assembly comprising a driving rotor and a driven rotor, the driving rotor and the driven rotor being both located within the containing cavity, the driving rotor, the driven rotor and the wall face of the containing cavity jointly defining a variable-volume cavity, the driving rotor being capable of driving the driven rotor to rotate, and when the driving rotor drives the driven rotor to rotate, the volume of the variable-volume cavity changing; a transmission shaft, the transmission shaft passing through the through hole, one part of the transmission shaft being located within the mounting cavity, and the other part of the transmission shaft extending into the containing cavity and being connected to the driving rotor; and a sealing ring, the sealing ring being used for sealing a gap between the transmission shaft and the hole wall of the through hole or being used for sealing a gap between the transmission shaft and the inner wall of the mounting cavity. The present application can reduce the risk of fluid leakage from transmission shaft parts.

Description

Spherical rotor pump and teeth cleaning device

[0001] This application claims priority to the Chinese patent application filed with the Patent Office of China on January 31, 2024, with application number 202410141398.4 and invention name “Spherical rotor pump and tooth cleaning device”, and the Chinese patent application filed with the Patent Office of China on August 23, 2024, with application number 202422068711.4 and invention name “Water pump and oral care equipment”. The entire contents of the above two patent applications are incorporated into this application by reference. Technical Field

[0002] The present application relates to the field of oral cleaning technology, and in particular to a spherical rotor pump and a teeth cleaning device. Background Art

[0003] A spherical rotor pump is a positive displacement liquid delivery device. It typically consists of a pump casing and a rotor assembly housed within it. The rotor assembly rotates to pump water. During operation, the rotor assembly rotates at high speed within the pump casing. A precise fit between the rotor assembly and the pump casing is essential for sealing the gaps within the pump. Therefore, spherical rotor pump components are typically precision-manufactured.

[0004] However, precision manufacturing also brings with it complex processes, long manufacturing cycles, and high costs. Some manufacturers have switched to batch production of some components using molds, streamlining the process, improving production efficiency, and reducing costs. However, this reduced component precision can easily lead to seal failure within the pump. When this occurs, the fluid within the pump can easily overflow from the drive shaft during movement of the rotor assembly relative to the pump casing, causing leakage. Summary of the Invention

[0005] The present application provides a spherical rotor pump and a teeth cleaning device, which are intended to reduce the risk of liquid in the pump overflowing from the transmission shaft.

[0006] The specific technical solutions are as follows:

[0007] In a first aspect, an embodiment of the present application provides a spherical rotor pump, comprising: a pump casing, the pump casing having an accommodating chamber and an installation chamber, the accommodating chamber and the installation chamber being separated by a partition, the partition being provided with a through hole; a rotor assembly, the rotor assembly comprising 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 of the accommodating chamber jointly defining a variable capacity chamber, the active rotor being capable of driving 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 installation 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 installation chamber.

[0008] The spherical rotor pump in the embodiment of the present application has a housing having a housing cavity and a mounting cavity, the housing cavity and the mounting cavity being separated by a partition, the rotor assembly being located in the housing cavity, and the drive shaft passing through a through hole provided on the partition to connect with the active rotor in the housing cavity. The spherical rotor pump is also provided with a sealing ring, which is used to seal the gap between the drive shaft and the hole wall of the through hole, or to seal the gap between the drive shaft and the inner wall of the mounting cavity. In this way, even if the gap seal between the rotor assembly and the inner wall of the housing cavity fails, the risk of liquid overflowing from the drive shaft can be reduced.

[0009] In a second aspect, the present application provides a teeth cleaning device, which includes the spherical rotor pump in any of the above embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0011] FIG1 is a schematic structural diagram of a spherical rotor pump provided in one embodiment of the present application;

[0012] FIG2 is a schematic structural diagram of a spherical rotor pump provided in one embodiment of the present application from another perspective;

[0013] FIG3 is a schematic cross-sectional view of the structure shown in FIG2 taken along section AA in one embodiment;

[0014] FIG4 is a schematic cross-sectional view of the structure shown in FIG2 taken along section AA in another embodiment;

[0015] FIG5 is a schematic diagram of an isolation element provided in one embodiment of the present application;

[0016] FIG6 is a schematic structural diagram of a sealing ring provided in one embodiment of the present application;

[0017] FIG7 is a schematic cross-sectional view of a sealing ring provided in one embodiment of the present application;

[0018] FIG8 is a schematic structural diagram of a spherical rotor pump provided in another embodiment of the present application;

[0019] FIG9 is a schematic structural diagram of a spherical rotor pump provided in another embodiment of the present application from another perspective;

[0020] FIG10 is a schematic cross-sectional view of the structure shown in FIG9 along the line BB;

[0021] FIG11 is a schematic cross-sectional view of the structure shown in FIG2 taken along section AA in another embodiment;

[0022] FIG12 is an exploded schematic diagram of a spherical rotor pump provided in one embodiment of the present application;

[0023] FIG13 is an exploded schematic diagram of a partial structure of a spherical rotor pump provided in one embodiment of the present application;

[0024] FIG14 is a schematic structural diagram of a rotor assembly provided in one embodiment of the present application;

[0025] FIG15 is a schematic structural diagram of a driven rotor provided in one embodiment of the present application;

[0026] FIG16 is a schematic structural diagram of an active rotor provided in one embodiment of the present application;

[0027] FIG17 is a schematic structural diagram 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);

[0028] FIG18 is a schematic cross-sectional view of the structure shown in FIG2 taken along section AA in another embodiment;

[0029] FIG19 is a schematic cross-sectional view of the structure shown in FIG7 taken along line BB in another embodiment;

[0030] FIG20 is a schematic diagram of the connection structure between the output shaft and the transmission shaft of the driving device provided in one embodiment of the present application;

[0031] FIG21 is a schematic diagram of a driving device provided in one embodiment of the present application;

[0032] FIG22 is a schematic diagram of a transmission shaft provided in one embodiment of the present application;

[0033] FIG23 is a schematic diagram of the connection structure between the output shaft and the transmission shaft of a driving device provided by another embodiment of the present application;

[0034] FIG24 is a schematic diagram of a driving device provided by another embodiment of the present application;

[0035] FIG25 is a schematic diagram of a transmission shaft provided by another embodiment of the present application;

[0036] FIG26 is an enlarged schematic diagram of portion B in FIG3 ;

[0037] FIG27 is a partial enlarged schematic diagram of the structure shown in FIG3 (the sealing member is hidden);

[0038] FIG28 is an enlarged schematic diagram of portion C in FIG27 ;

[0039] FIG29 is an exploded schematic diagram of a spherical rotor pump provided in one embodiment of the present application;

[0040] FIG30 is a schematic structural diagram of a first housing provided in one embodiment of the present application;

[0041] FIG31 is a partial enlarged schematic diagram of FIG3;

[0042] FIG32 is a schematic diagram of a rotor assembly provided in one embodiment of the present application;

[0043] FIG33 is a schematic diagram of a driven rotor provided in one embodiment of the present application;

[0044] FIG34 is a schematic diagram of a driven rotor provided by an embodiment of the present application from another perspective;

[0045] FIG35 is a schematic diagram of an active rotor provided in one embodiment of the present application;

[0046] FIG36 is a schematic diagram of the internal structure of a teeth cleaning device provided in one embodiment of the present application;

[0047] FIG37 is a schematic diagram of the external structure of a teeth cleaning device provided in one embodiment of the present application;

[0048] FIG38 is a schematic diagram showing the connection between the spherical rotor pump, the liquid storage tank, and the nozzle of the tooth cleaning device provided in one embodiment of the present application;

[0049] FIG39 is a schematic structural diagram of a spherical rotor pump provided in one embodiment of the present application;

[0050] FIG40 is another schematic structural diagram of a spherical rotor pump provided in one embodiment of the present application;

[0051] FIG41 is a schematic diagram of a partial cross-sectional structure along line AA in FIG3 ;

[0052] FIG42 is a schematic diagram of a partially exploded structure of a spherical rotor pump provided in one embodiment of the present application;

[0053] FIG43 is a schematic structural diagram of a first housing provided in one embodiment of the present application;

[0054] Figure 44 is a schematic cross-sectional structural diagram of a rotor assembly provided in one embodiment of the present application. DETAILED DESCRIPTION

[0055] In order to make the purpose, technical solutions and advantages of this application more clearly understood, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this application and are not intended to limit this application.

[0056] A spherical rotor pump is a positive displacement liquid delivery device. It typically consists of a pump casing and a rotor assembly housed within it. The rotor assembly rotates to pump water. During operation, the rotor assembly rotates at high speed within the pump casing. A precise fit between the rotor assembly and the pump casing is essential for sealing the gaps within the pump. Therefore, spherical rotor pump components are typically precision-manufactured.

[0057] However, precision manufacturing also brings with it complex processes, long manufacturing cycles, and high costs. Some manufacturers have switched to batch production of some components using molds, streamlining the process, improving production efficiency, and reducing costs. However, this reduced component precision can easily lead to seal failure within the pump. When this occurs, the fluid within the pump can easily overflow from the drive shaft during movement of the rotor assembly relative to the pump casing, causing leakage.

[0058] 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 drive shaft.

[0059] As shown in Figures 1, 2 and 3, the spherical rotor pump 100 provided in the embodiment of the first aspect 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 accommodating chamber 101 and an installation chamber 102, and the accommodating chamber 101 and the installation 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 accommodating chamber 101. The active rotor 201, the driven rotor 202 and the wall surface of the accommodating chamber 101 jointly define a variable capacity chamber 203. 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 capacity chamber 203 changes. The transmission shaft 3 passes through the through hole 104. A portion of the transmission shaft 3 is located within the mounting cavity 102, while the other portion of the transmission shaft 3 extends into the accommodating cavity 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 wall of the through hole 104, or to seal the gap between the transmission shaft 3 and the inner wall of the mounting cavity 102.

[0060] 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 to 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.

[0061] 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 being 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 the gap seal between the rotor assembly 2 and the inner wall of the housing chamber 101 fails, the risk of liquid overflowing from the transmission shaft 3 can be reduced.

[0062] In some embodiments, as shown in Figure 3, the sealing ring 4 is disposed in the installation cavity 102, and the sealing ring 4 is sleeved on the transmission shaft 3. This arrangement allows the sealing ring 4 to seal one side of the installation cavity 102 to reduce the risk of liquid overflow.

[0063] Specifically, the sealing ring 4 can abut against the partition 103 , thereby sealing the gap between the transmission shaft 3 and the through hole 104 .

[0064] Alternatively, the sealing ring 4 may 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 .

[0065] Furthermore, as shown in FIG3 , the spherical rotor pump 100 may also include a bearing 6 and an isolator 7. The bearing 6 is located in the mounting 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 is in contact with the wall of the mounting cavity 102, and the isolator 7 is located between the bearing 6 and the sealing ring 4. By providing the bearing 6 sleeved on the transmission shaft 3 and making the bearing 6 contact with the wall of the mounting 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 drive device 5 driving the transmission shaft 3 to rotate, the position of the transmission shaft 3 can also be ensured not to shift, thereby improving the position stability of the transmission shaft 3. In addition, the isolator 7 is used to isolate the bearing 6 from the sealing ring 4. In this way, it can be ensured that the bearing 6 does not affect the sealing ring 4 when it moves, thereby avoiding the displacement of the sealing ring 4 and affecting the sealing performance.

[0066] Furthermore, as shown in Figure 3, the installation cavity 102 includes a first section 109 and a second section 110 that 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.

[0067] 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 keeping the sealing ring 4 in a compressed state, thereby better exerting the sealing performance. 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 members 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 members 7 from excessively squeezing the sealing ring 4, thereby causing excessive friction between the sealing ring 4 and the transmission shaft 3.

[0068] 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 size of the sealing ring 4 along the axial direction of the transmission shaft 3 is larger than the size of the first section 109 along the axial direction of the transmission shaft 3.

[0069] It is understood that when the sealing ring 4 is uncompressed (in its natural state), its dimension along the axis of the transmission shaft 3 is greater than the dimension of the first section 109 along the axis of the transmission shaft 3. When the sealing ring 4 is installed in the first section 109, the sealing ring 4 is compressed along the axis of the transmission shaft 3, causing extrusion deformation, which helps improve the sealing performance of the sealing ring 4.

[0070] In one embodiment, as shown in Figures 3 and 5, 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 gap 701 is formed on the side of the gasket close to the bearing 6. The avoidance gap 701 is arranged opposite to the bearing inner ring 601 to avoid the bearing inner ring 601.

[0071] It is understood that when the transmission shaft 3 rotates, the bearing inner ring 601 rotates with the transmission shaft 3, while the bearing outer ring 602 remains stationary. When the spacer 7 is an annular gasket with an inner diameter smaller than the outer diameter of the bearing inner ring 601, a relief notch 701 can be provided on the side of the gasket closest to the bearing 6 to prevent the gasket from contacting the bearing inner ring 601. This prevents the wall bearing inner ring 601 from rubbing against the gasket during rotation.

[0072] 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. 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 radially spaced apart.

[0073] 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 and the bearing inner ring 601 do not come into contact. In this way, friction between the bearing inner ring 601 and the gasket during rotation can be avoided.

[0074] In other embodiments, as shown in FIG4 , a sealing ring 4 is disposed within the accommodating cavity 101, sleeved around the transmission shaft 3, and abutting against the partition 103. This configuration allows the sealing ring 4 to seal the gap between the transmission shaft 3 and the wall of the through hole 104 from one side of the accommodating cavity 101, thereby reducing the risk of liquid overflowing into the mounting cavity 102.

[0075] Furthermore, a first placement groove 105 can 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, which helps to keep the position stability of the sealing ring 4.

[0076] Furthermore, as shown in FIG4 , the spherical rotor pump 100 may further include an anti-wear pad 8 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 during rotation, thereby preventing the sealing ring 4 from wearing or shifting.

[0077] Furthermore, a second mounting groove 106 is provided in the accommodating chamber 101. The second mounting groove 106 communicates with the first mounting groove 105. Part of the structure of the anti-wear gasket 8 is located in the second mounting groove 106. The radial dimension of the first mounting groove 105 is smaller than the radial dimension of the second mounting groove 106. This arrangement allows the anti-wear gasket 8 to be positioned by the second mounting groove, thereby maintaining the positional stability of the anti-wear gasket 8. In addition, the anti-wear gasket 8 can also be used to block the sealing ring 4, thereby ensuring that the sealing ring 4 is always retained in the first mounting groove 105.

[0078] Furthermore, the thickness of the anti-wear pad 8 is greater than the depth of the second seating groove 106, allowing a portion of the anti-wear pad 8 to extend outside the second seating groove 106. Thus, the rotor assembly 2 abuts the portion of the anti-wear pad 8 extending outside the second seating groove 106, compressing the portion of the anti-wear pad 8 within the second seating groove 106. The compressed anti-wear pad 8 further compresses the sealing ring 4 within the first seating groove 105. This ensures a tight fit between the sealing ring 4 and the partition 103, improving the sealing performance of the sealing ring 4.

[0079] Furthermore, as shown in Figures 3 and 4, the rotor assembly 2 includes a driving rotor 201 and a driven rotor 202. Both the driving rotor 201 and the driven rotor 202 are located within the accommodating chamber 101, and the drive shaft 3 is connected to the driving rotor 201. A limit end surface is provided on the end of the driving rotor 201 proximate to the anti-wear pad 8. The limit end surface is flat and abuts against the anti-wear pad 8. In this embodiment, the limit end surface is provided on the end of the driving rotor 201 proximate to the anti-wear pad 8. The limit end surface is flat and abuts against the anti-wear pad 8, thereby improving the uniformity of the force applied to the anti-wear pad 8.

[0080] Furthermore, as shown in Figures 3 and 4, a limiting portion 2012 is formed on one end of the driving rotor 201 away from the driven rotor 202, and a limiting end surface is formed on the limiting portion 2012. A third seating groove 150 is also provided within the accommodating chamber 101. The third seating groove 150 communicates with the second seating groove 106. The limiting portion 2012 is located within the third seating groove 150. The radial dimension of the second seating groove 106 is smaller than that of the third seating groove 150. Forming the limiting portion 2012 on the driving rotor 201 and positioning it within the third seating groove 150 facilitates maintaining a predetermined posture of the driving rotor 201 within the accommodating chamber 101, preventing the driving rotor from generating unexpected rotational motion.

[0081] 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 larger than the size of the first mounting groove 105 along the axial direction of the transmission shaft 3.

[0082] It is understood that when the sealing ring 4 is uncompressed (in its natural state), its dimension along the axis of the transmission shaft 3 is greater than the dimension of the first seating groove 105 along the axis of the transmission shaft 3. When the sealing ring 4 is installed in the first seating groove 105, the sealing ring 4 is compressed along the axis of the transmission shaft 3, causing extrusion deformation, which helps improve the sealing performance of the sealing ring 4.

[0083] In some embodiments, as shown in Figures 6 and 7, the sealing ring 4 is a Y-shaped sealing ring, which includes a sealing ring body 401. 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, which can improve the sealing between the sealing ring 4 and the partition 103, thereby further reducing the possibility of the liquid in the accommodating chamber 101 leaking through the through hole 104.

[0084] In some embodiments, the pump housing 1 includes a first housing 107 and a second housing 108, which are connected to each other. The first housing 107 and the second housing 108 together define a receiving chamber 101, and the second housing 108 defines a mounting chamber 102. The spherical rotor pump 100 also includes a drive device 5, which 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 chamber 102 and connected to the transmission shaft 3.

[0085] In some embodiments, as shown in Figures 8, 9, and 10, the spherical rotor pump 100 further includes a bearing 6, which is located within the mounting cavity 102. The bearing 6 is sleeved on the transmission shaft 3 and / or the output shaft 501. The bearing 6 is disposed on the side of the sealing ring 4 away from the partition 103, and the bearing 6 contacts the wall of the mounting cavity 102. The spherical rotor pump 100 further includes a support block 9, which is disposed on the side of the bearing 6 away from the partition 103 and is fixed within the mounting cavity 102.

[0086] 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 is 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.

[0087] In addition, by sleevedly 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 drive 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.

[0088] Furthermore, spherical rotor pump 100 includes a support block 9, which is disposed on the side of bearing 6 away from partition 103 and is secured within mounting cavity 102. Support block 9 blocks foreign matter on the side of bearing 6 away from partition 103, thereby preventing foreign matter from contacting bearing 6 and adversely affecting its performance.

[0089] In some embodiments, the main body 502 has an end face 503 set toward the pump casing 1, and the end face 503 is formed with a protruding structure 504. The protruding structure 504 is located in the installation cavity 102, and the support block 9 is against the protruding structure 504; the radial dimension of the support block 9 is larger than the radial dimension of the protruding structure 504.

[0090] By abutting the support block 9 against the raised structure 504 on the end of the main body 502, the support block 9 and the raised structure 504 together form a barrier structure for blocking external debris. This barrier structure not only blocks 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 raised structure 504. This helps to reduce the contact area between the two, thereby increasing the pressure between the two and ensuring a closer contact between the two.

[0091] 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.

[0092] In some embodiments, as shown in FIG. 3 or FIG. 4 , the active rotor 201 includes a first support member 204 and a first encapsulated body 205 . The first support member 204 is encapsulated within the first encapsulated body 205 to serve as the inner skeleton of the active rotor 201 . The transmission shaft 3 extends into the first encapsulated body 205 and is connected to the first support member 204 .

[0093] In this embodiment, the driving rotor 201 includes a first support member 204 and a first encapsulated body 205 surrounding the first support member 204. The first support member 204 can be made of a high-strength material, such as metal. This improves the overall structural strength of the driving rotor 201, while the first encapsulated body 205 effectively seals the gap with the inner wall of the pump casing 1. Furthermore, the drive shaft 3 extends into the first encapsulated body 205 and connects to the first bearing 6. This improves the connection strength between the drive shaft 3 and the driving rotor 201, thereby enhancing transmission stability.

[0094] It is understandable that the transmission shaft 3 can also be made of a material with higher strength, such as a metal material. In this way, the transmission shaft 3 can have better structural strength, thereby being able to transmit more stably.

[0095] 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 through the same manufacturing process (such as metal casting).

[0096] In some embodiments, the driven rotor 202 includes a second support member 206 and a second encapsulated body 207, which at least partially covers the second support member 206. In this embodiment, the driven rotor 202 includes the second support member 206 and the second encapsulated body 207, which at least partially covers the second support member 206. The second support member 206 can be made of a high-strength material, such as metal. This improves the overall structural strength of the driven rotor 202, while the second encapsulated body 207 effectively seals the gap with the inner wall of the pump housing 1.

[0097] In some embodiments, as shown in FIG11 , 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 axis.

[0098] Due to the limitation of machining precision, there may be space for movement after the rotor assembly 2 and the pump housing 1 are assembled, which makes the rotor assembly 2 prone to axial movement, thereby increasing the friction between the rotor assembly 2 and the pump housing 1.

[0099] 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, thereby reducing the possibility of axial movement of the active rotor 201, thereby improving the problem of axial movement of the rotor assembly 2.

[0100] In some embodiments, as shown in FIG11 , the pump housing 1 forms a limiting surface 111, and the limiting structure 10 includes a first member 1001, a second member 1002, and a gasket 1004. The first member 1001 is connected to the transmission shaft 3 so that the first member 1001 is fixed relative to the transmission shaft 3 along the axial direction of the transmission shaft 3. The second member 1002 is fixedly connected to the pump housing 1. The gasket 1004 abuts against the limiting surface 111, and the first member 1001 is confined between the gasket 1004 and the second member 1002.

[0101] The first component 1001 is confined between the gasket 1004 and the second component 1002, so that the movement of the first component 1001 along the axis of the transmission shaft 3 is restricted. In addition, 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 is restricted.

[0102] In one embodiment, as shown in Figure 11 , the first component 1001 is a bearing 6 mounted on the transmission shaft 3. In this embodiment, the bearing 6 mounted on the transmission shaft 3 is confined between the spacer 1004 and the second component 1002, thereby limiting the movement of the transmission shaft 3 along its axis. Furthermore, the bearing 6 can contact the wall of the pump housing 1. This improves the centering accuracy of the transmission shaft 3 during installation. Furthermore, the position of the transmission shaft 3 is prevented from shifting during rotation by the drive device 5, thereby improving the positional stability of the transmission shaft 3.

[0103] Furthermore, the bearing 6 includes an outer ring 602 and an inner ring 601 connected to the outer ring 602. The inner ring 601 is fastened to the transmission shaft 3, securing the bearing 6 relative to the transmission shaft 3 along its axis. One end of the outer ring 602 abuts against the gasket 1004, while the other end abuts against the second member 1002. In other words, the outer ring 602 is trapped between the gasket 1004 and the second member 1002. This restricts the movement of the transmission shaft 3 relative to the pump housing 1 along its axis.

[0104] Furthermore, as shown in FIG11 , the limiting structure 10 may further include a third member 1003, which is fixedly connected to the transmission shaft 3 and abuts against an end of the bearing inner ring 601 that is away from the gasket 1004. The provision of the third member 1003 further ensures axial stability between the transmission shaft 3 and the bearing 6, preventing the tight fit between the bearing inner ring 601 and the transmission shaft 3 from loosening, thereby preventing the transmission shaft 3 from moving relative to the bearing 6.

[0105] 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 mounted on the transmission shaft 3. Using the pin as the third member 1003 has the advantage of a stable connection.

[0106] 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. In this case, the retaining spring 11 or the pin sleeved on the transmission shaft 3 is restrained between the washer 1004 and the second member 1002, thereby limiting the movement of the transmission shaft 3 along its own axis.

[0107] In some embodiments, as shown in FIG11 , 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, easy material acquisition, and low cost.

[0108] Furthermore, as shown in Figure 11, the pump housing 1 also has an installation cavity 102, the limiting structure 10 is located in the installation cavity 102, a portion of the drive shaft 3 is located in the accommodating cavity 101, and another portion of the drive shaft 3 is located in the installation cavity 102, and the retaining 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 portion of the drive shaft 3 are also located in the installation cavity 102, so that the limiting structure 10 and the drive 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 drive shaft 3, the limiting structure 10, etc. On this basis, the snap ring 12 can be interference-fitted with the mounting cavity 102 to achieve a fixed connection between the second component 1002 (snap ring 12 ) and the pump housing 1 .

[0109] In some embodiments, as shown in Figures 11, 12, 13, and 14, the driving rotor 201 and the driven rotor 202 are connected by a pin 208, so that the driven rotor 202 can rotate about the pin 208 relative to the driving rotor 201. In this embodiment, the driving rotor 201 and the driven rotor 202 are connected by the pin 208, so that the driving rotor 201 and the driven rotor 202 are connected together. This arrangement makes the driving rotor 201 and the driven rotor 202 form an integral structure. In this way, on the basis of the limiting structure 10 limiting the movement of the drive shaft 3 relative to the pump housing 1 along its own axis, the possibility of movement of the driving rotor 201 and the driven rotor 202 is reduced, thereby improving the positional stability of the driving rotor 201 and the driven rotor 202 relative to the pump housing 1.

[0110] In some embodiments, as shown in Figures 11, 15, 16, and 17, the active rotor 201 includes a first support member 204 and a first encapsulated body 205. A portion of the first support member 204 is encapsulated within the first encapsulated body 205, serving as the inner skeleton of the active rotor 201. Another portion of the first support member 204 is located outside the first encapsulated body 205, forming a connecting portion 2041. The driven rotor 202 includes a second support member 206 and a second encapsulated body 207, with the second encapsulated body 207 covering at least a portion of the second support member 206. A through slot 2071 is provided in the second encapsulated body 207. The connecting portion 2041 extends through the through slot 2071 into the interior of the second encapsulated body 207 and is connected to the second support member 206 via a pin 208.

[0111] 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 relatively strong material, thereby improving the overall structural strength of the active rotor 201. The exterior of the active rotor 201 is the first encapsulated body 205, which 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 relatively strong material, thereby improving the overall structural strength of the driven rotor 202. The exterior of the driven rotor 202 is the second encapsulated body 207, which can better form a gap seal with the inner wall of the pump housing 1.

[0112] Furthermore, a portion of the first support member 204 is enclosed within the first encapsulated body 205, while another portion is located outside the first encapsulated body 205, forming a connecting portion 2041. A through-slot 2071 is provided in the second encapsulated body 207. The connecting portion 2041 extends through the through-slot 2071 into the second encapsulated body 207 and is connected to the second support member 206 via a pin 208. This arrangement connects the first support member 204 and the second support member 206 via the pin 208, thereby achieving a connection between the driving rotor 201 and the driven rotor 202, forming a single, integrated structure.

[0113] Furthermore, as shown in FIG11 , 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 sidewalls of the through slot 2071. This arrangement provides the connecting portion 2041 with a certain amount of swing space, thereby preventing interference between the connecting portion 2041 and the second encapsulated body 207 when the driving rotor 201 drives the driven rotor 202 to rotate.

[0114] In some embodiments, as shown in Figure 12, 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.

[0115] In this embodiment, the first axis a of the driving rotor 201 intersects the second axis b of the driven rotor 202, and the pin 208 intersects both the first axis a and the second axis b. When the driving rotor 201 drives the driven rotor 202 to rotate, the driving rotor 201 continuously rotates around the first axis, while the driven rotor 202 continuously rotates around the second axis b. Simultaneously, the driven rotor 202 performs a reciprocating oscillating motion around the pin 208. During this process, the volume of the variable capacity chamber 203, defined by the driving rotor 201, the driven rotor 202, and the wall of the accommodating chamber 101, can change.

[0116] In some embodiments, as shown in Figures 12, 14, 15 and 16, a groove 210 is provided on the driven rotor 202, and a pin portion 209 is formed on the driving rotor 201. The surface of the pin portion 209 is a cylindrical surface or a semi-cylindrical surface. The pin 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 208 coincides with the third axis c.

[0117] The mating of the pin portion 209 and the groove 210 creates a seal between the active rotor 201 and the driven rotor 202, thereby defining a sealed variable capacity chamber 203 between the active rotor 201, the driven rotor 202, and the wall of the accommodating chamber 101. Furthermore, the pin portion 209 is confined within the groove 210 and is capable of rotating relative to the groove 210 about the third axis c. Specifically, the third axis c serves as the rotation center of the pin portion 209. Furthermore, the central axis of the pin 208 coincides with the third axis c. This ensures that the pin portion 209 remains in a well-fitted relationship with the groove 210 during the reciprocating swinging motion of the driven rotor 202 about the pin 208, thereby maintaining a good seal between the active rotor 201 and the driven rotor 202. Furthermore, the coincidence of the central axis of the pin 208 with the third axis c also facilitates smooth movement of the rotor assembly 2 and prevents any jamming.

[0118] In some embodiments, the spherical rotor pump 100 further includes a drive device 5 and a constraint structure 13. The drive device 5 has an output shaft 501 that 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.

[0119] Spherical rotor pumps in the related art are prone to rotor assembly rotation problems, which can lead to pump jamming in severe cases. The primary cause of this rotor assembly friction in spherical rotor pumps is poor coaxiality between the output shaft of the drive unit and the transmission shaft. This causes the rotor assembly to deviate from its intended position, leading to rotational problems and, in severe cases, pump jamming. Furthermore, this deviation from the intended position increases friction between the rotor assembly and the pump casing.

[0120] The spherical rotor pump 100 in this embodiment is equipped with a restraining structure 13. This restraining structure 13 is mounted over the transmission shaft 3 and the output shaft 501 of the drive unit 5 to secure the output shaft 501 and transmission shaft 3. The restraining effect of the restraining structure 13 improves the coaxiality between the output shaft 501 of the drive unit 5 and the transmission shaft 3. This reduces or eliminates the deviation between the actual and expected positions of the rotor assembly 2, allowing the rotor assembly 2 to rotate more smoothly. This helps prevent pump jams and increased friction between the rotor assembly 2 and the pump housing 1.

[0121] Furthermore, as shown in FIG18 , the pump housing 1 further comprises a mounting cavity 102, within which the output shaft 501 and the restraining structure 13 are both located. A portion of the transmission shaft 3 is located in the mounting cavity 102, while another portion of the transmission shaft 3 extends into the accommodating cavity 101. The restraining structure 13 is a sleeve 14, with a gap between the outer wall of the sleeve 14 and the wall of the mounting cavity 102.

[0122] In this embodiment, the pump housing 1 has a accommodating cavity 101 and a mounting cavity 102. The accommodating cavity 101 is used to accommodate the rotor assembly 2, and the mounting cavity 102 can be used to accommodate the output shaft 501 of the drive device 5. In this way, the mounting cavity 102 can be used to protect the output shaft 501 of the drive device 5. At the same time, the constraint structure 13 and a portion of the transmission shaft 3 are also located in the mounting cavity 102, so that the constraint structure 13 and the transmission shaft 3 can also be under the protection of the mounting cavity 102. In addition, in this embodiment, the constraint structure 13 is a sleeve 14 that is sleeved on the output shaft 501 and the transmission shaft 3. The sleeve 14 can keep the axis of the output shaft 501 and the axis of the transmission shaft 3 collinear. In addition, there is a gap between the outer wall of the sleeve 14 and the wall of the mounting cavity 102. In this way, when the sleeve 14 rotates with the output shaft 501 and the transmission shaft 3, it will not generate friction with the wall of the mounting cavity 102.

[0123] Furthermore, as shown in FIG18 , the spherical rotor pump 100 may further include a bearing 6 sleeved on the transmission shaft 3. The bearing 6 is located within the mounting cavity 102, with the outer wall of the bearing 6 contacting the wall of the mounting cavity 102. By providing the bearing 6 sleeved on the transmission shaft 3 and ensuring that the bearing 6 contacts the wall 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 positional accuracy of the transmission shaft 3. Furthermore, the position of the transmission shaft 3 can be maintained without displacement during the process of the drive device 5 driving the transmission shaft 3 to rotate.

[0124] Furthermore, as shown in FIG18 , a limiting surface 111 is formed within the mounting cavity 102. The spherical rotor pump 100 further includes a snap ring 12, a gasket 23, and a retaining spring 11. The gasket 23 abuts the limiting surface 111, the snap ring 12 has an interference fit with the mounting cavity 102, and the retaining 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 the gasket 23, and the other end of the bearing outer ring 602 abuts the snap ring 12. The retaining spring 11 abuts the end of the bearing inner ring 601 away from the gasket 23.

[0125] Bearing 6 includes an inner ring 601 and an outer ring 602. The inner ring 601 is secured to the drive shaft 3, securing the bearing 6 relative to the drive shaft 3 in its axial direction. The outer ring 602 is confined between a gasket 23 and a retaining ring 12. The gasket 23 abuts against a limiting surface 111 of the mounting cavity 102, while the retaining ring 12 forms an interference fit with the mounting cavity 102. This effectively limits the axial movement of the drive shaft 3 relative to the pump housing 1. Since the drive shaft 3 is connected to the active rotor 201, the possibility of axial movement of the active rotor 201 is reduced, thereby avoiding the problem of increased friction between the active rotor 201 and the pump housing 1 caused by axial movement. Furthermore, the provision of a retaining ring 11 further ensures axial stability between the drive shaft 3 and the bearing 6, preventing the tight fit between the inner ring 601 and the drive shaft 3 from loosening, which could cause the drive shaft 3 to move relative to the bearing 6.

[0126] In other embodiments, as shown in FIG19 , the pump housing 1 further comprises a mounting cavity 102, wherein the output shaft 501 and the restraining structure 13 are both located within the mounting cavity 102. A portion of the transmission shaft 3 is located within the mounting cavity 102, while another portion of the transmission shaft 3 extends into the accommodating cavity 101. The restraining structure 13 is a bearing 6, which is located within the mounting cavity 102, with the outer wall of the bearing 6 contacting the wall of the mounting cavity 102.

[0127] In this embodiment, the constraint structure 13 is a bearing 6 sleeved on the output shaft 501 and the transmission shaft 3. Using the bearing 6 as the constraint structure 13 not only maintains the axis of the output shaft 501 and the axis of the transmission shaft 3 in alignment, but also, by allowing the outer wall of the bearing 6 to contact the wall of the mounting cavity 102, improves the centering accuracy of the transmission shaft 3 relative to the mounting cavity 102, thereby further improving the positioning accuracy of the transmission shaft 3. In this embodiment, since the bearing 6 not only improves the centering accuracy of the transmission shaft 3 but also serves as the constraint structure 13, this arrangement reduces the number of components, thereby facilitating a reduction in the overall dimensions of the spherical rotor pump 100 along the axis of the transmission shaft 3.

[0128] Furthermore, as shown in Figure 19 , the drive device 5 further includes a main body 502, with the output shaft 501 connected to the main body 502. A limiting surface 111 is formed within the mounting cavity 102. The spherical rotor pump 100 further includes a support block 9, which is located within the mounting cavity 102 and abuts against the main body 502. The bearing 6 is confined between the limiting surface 111 and the support block 9.

[0129] In this embodiment, the bearing 6 is tightly sleeved on the transmission shaft 3. At the same time, the bearing 6 is confined between the limiting surface 111 of the mounting cavity 102 and the support block 9. Thus, 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 axial movement.

[0130] In some embodiments, as shown in Figures 20, 21, and 22, the output shaft 501 includes a first mating portion 5011, which is provided with a first contact surface 5012. The transmission shaft 3 includes a second mating portion 301, which is provided with a second contact surface 3011. The first contact surface 5012 and the second contact surface 3011 are tightly abutted against each other, thereby enabling torque transmission between the output shaft 501 and the transmission shaft 3. With the constraint structure 13 sleeved on the output shaft 501 and the transmission shaft 3, the first contact surface 5012 of the first mating portion 5011 and the second contact surface 3011 of the second mating portion 301 are tightly abutted against each other. This arrangement enables a transmission connection between the output shaft 501 and the transmission shaft 3. Furthermore, this arrangement is simple in structure and easy to process and implement.

[0131] Furthermore, the first contact surface 5012 and the second contact surface 3011 are both planes, which helps to better fit the first contact surface 5012 and the second contact surface 3011 to each other, thereby helping to prevent the output shaft 501 and the transmission shaft 3 from shaking or vibrating during the transmission process.

[0132] Furthermore, the cross-sectional shape of the first mating portion 5011 is a first semicircle, and the cross-sectional shape of the second mating portion 301 is a second semicircle, with the radius of the first semicircle being equal to the radius of the second semicircle. Thus, when the first contact surface 5012 of the first mating portion 5011 and the second contact surface 3011 of the second mating portion 301 are tightly abutted, the first mating portion 5011 and the second mating portion 301 can be assembled into a complete cylinder, with the axis of the cylinder coinciding with the axis of the output shaft 501 and the axis of the transmission shaft 3.

[0133] In other embodiments, the output shaft 501 includes a third mating portion, and the transmission shaft 3 includes a fourth mating portion. One of the third and fourth mating portions is a prismatic structure, and the other is a mounting sleeve. The mounting sleeve has an inner cavity whose shape matches the prismatic structure, and the prismatic structure fits within the inner cavity. In this embodiment, the output shaft 501 and the transmission shaft 3 utilize a prismatic structure and an inner cavity that match the prismatic structure. For example, when the prismatic structure is a quadrangular prism, the inner cavity has a quadrilateral cross-section, and when the prismatic structure is a hexagonal prism, the inner cavity has a hexagonal cross-section. This arrangement enables torque to be transmitted between the output shaft 501 and the transmission shaft 3, allowing the output shaft 501 to drive the transmission shaft 3 in rotation. Furthermore, this arrangement ensures that the forces on the output shaft 501 and the transmission shaft 3 are more evenly distributed during transmission.

[0134] Furthermore, the prismatic structure is a regular prism, and the number of side faces of the regular prism is greater than or equal to 3 and less than or equal to 6. The regular prism structure further improves the uniformity of force applied to the output shaft 501 and the transmission shaft 3 during transmission, thereby extending the service life of the output shaft 501 and the transmission shaft 3. Furthermore, the number of side faces of the regular prism is between 3 and 6, making the prismatic structure easier to manufacture and also improving the machining accuracy of the prismatic structure.

[0135] In other embodiments, as shown in Figures 23, 24, and 25, one of the output shaft 501 and the transmission shaft 3 is provided with a retaining groove 302, and the other of the output shaft 501 and the transmission shaft 3 is provided with a flat shaft portion 5013. The flat shaft portion 5013 cooperates with the retaining groove 302 to enable torque transmission between the output shaft 501 and the transmission shaft 3. In this embodiment, the cooperation between the flat shaft portion 5013 and the retaining groove 302 enables torque transmission between the output shaft 501 and the transmission shaft 3. Furthermore, this arrangement ensures that the forces acting on the output shaft 501 and the transmission shaft 3 are more evenly distributed during transmission.

[0136] Furthermore, one of the output shaft 501 and the transmission shaft 3 is provided with an axially extending mounting hole 303, and the other of the output shaft 501 and the transmission shaft 3 is provided with a mounting portion 5014 connected to the flat shaft portion 5013. The mounting portion 5014 has an interference fit with the mounting hole 303. The interference fit between the mounting portion 5014 and the mounting hole 303 maintains the output shaft 501 and the transmission shaft 3 relatively fixed in the axial direction. This also helps prevent axial movement of the transmission shaft 3, thereby reducing the possibility of axial movement of the driving rotor 201, and further avoiding the problem of increased friction between the driving rotor 201 and the pump housing 1 caused by axial movement of the driving rotor 201.

[0137] In some embodiments, as shown in Figures 3 and 26, the spherical rotor pump 100 further includes a seal 16. Specifically, the pump housing 1 includes a first housing 107 and a second housing 108 connected to the first housing 107. The first housing 107 and the second housing 108 together define an accommodating chamber 101. The rotor assembly 2 is located in the accommodating chamber 101. The seal 16 is located between the first housing 107 and the second housing 108 and is disposed around the accommodating chamber 101. 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.

[0138] In the embodiment of the present application, the pump housing 1 includes a first housing 107 and a second housing 108 that are connected to each other. A sealing member 16 is provided between the first housing 107 and the second housing 108, surrounding the accommodating chamber 101. This allows a seal to be formed between the first housing 107 and the second housing 108, thereby reducing the risk of liquid leakage from the accommodating chamber 101. In addition, a groove 121 and a protrusion 122 are provided at the contact portion between the first housing 107 and the second housing 108. The protrusion 122 extends into the groove 121 and presses the sealing member 16 into the groove 121. In this way, the sealing member 16 can be kept in a compressed state, thereby improving the sealing effect of the sealing member 16 and further reducing the risk of liquid leakage.

[0139] In some embodiments, as shown in FIG. 26 , FIG. 27 and FIG. 28 , the thickness h of the protrusion 122 gradually decreases in a direction away from the rotor assembly 2 .

[0140] Taking the example of groove 121 provided on first housing 107 and protrusion 122 provided on second housing 108, when first housing 107 and second housing 108 are assembled, protrusion 122 on second housing 108 presses against seal 16. Because the thickness h of protrusion 122 gradually decreases as it moves away from rotor assembly 2, protrusion 122 compresses seal 16 while simultaneously causing seal 16 to expand radially outward. This forces force from seal 16 on first housing 107, causing slight outward deformation of first housing 107 under the action of this force. This helps prevent compression between first housing 107 and rotor assembly 2, which could increase friction during rotation.

[0141] Taking the example of groove 121 provided on second housing 108 and protrusion 122 provided on first housing 107, when first housing 107 and second housing 108 are assembled, protrusion 122 on first housing 107 squeezes seal 16. Because the thickness h of protrusion 122 gradually decreases as it moves away from rotor assembly 2, protrusion 122 squeezes seal 16 while simultaneously causing seal 16 to expand radially outward. This forces the second housing 108 to be slightly deformed outward due to the force from seal 16. This helps prevent compression between second housing 108 and rotor assembly 2, which could increase friction during rotation.

[0142] In some embodiments, as shown in Figures 28 and 29, protrusion 122 is annular, allowing any position of seal 16 to be squeezed by protrusion 122. Furthermore, the cross-sectional shape of protrusion 122 can be trapezoidal, with the short base of the trapezoid corresponding to the surface of seal 16 away from rotor assembly 2, and the long base of the trapezoid corresponding to the surface of seal 16 closer to rotor assembly 2. This allows seal 16 to be constructed such that the thickness h of protrusion 122 gradually decreases as it moves away from rotor assembly 2.

[0143] 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 the second axis b.

[0144] In one embodiment, the end surface 1221 of the protrusion 122 is perpendicular to the second axis b. In this case, the thickness h of the protrusion 122 remains constant as it moves away from the rotor assembly 2, meaning that the protrusion 122 has a uniform thickness h. In this case, after the first shell 107 and the second shell 108 are assembled, the housing where the groove 121 is located will not deform slightly outward or inward, thereby preventing the housing where the groove 121 is located from being squeezed against the rotor assembly 2 after assembly.

[0145] In another embodiment, as shown in FIG27 , the angle β between the end surface 1221 of the protrusion 122 and the second axis b is greater than 90° and less than or equal to 135°. When the angle β between the end surface 1221 of the protrusion 122 and the second axis b is greater than 90°, the thickness h of the protrusion 122 gradually decreases as it moves away from the rotor assembly 2. In this case, when the first shell 107 and the second shell 108 are assembled, the shell in which the groove 121 is located will slightly deform outward. This helps prevent compression between the shell in which the groove 121 is located and the rotor assembly 2 after the first shell 107 and the second shell 108 are assembled, which could increase friction during rotation of the rotor assembly 2.

[0146] In some embodiments, as shown in FIG26 , the groove 121 includes a first portion 1211 and a second portion 1212 that are in communication with each other. The second portion 1212 is located on a side of the first portion 1211 away from the protrusion 122. The first portion 1211 is wider than the second portion 1212. The protrusion 122 is located within the first portion 1211, and the sealing member 16 is located at least within the second portion 1212. With this arrangement, during assembly of the first housing 107 and the second housing 108, the sealing member 16 is squeezed by the protrusion 122 and moves from the first portion 1211, which has a larger width, into the second portion 1212, which has a smaller width. Furthermore, the portion of the sealing member 16 located in the second portion 1212 is always kept in a compressed state. This further improves the sealing effect of the sealing member 16 and reduces the risk of liquid leakage.

[0147] In some embodiments, as shown in Figures 27 and 30, the first shell 107 and the second shell 108 each include a shell body 131 and a docking portion 132, the shell body 131 having an open end, and the docking portion 132 is located on the outside of 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 provided on the docking portion 132. By providing the docking portion 132 around the shell body 131 and connecting the docking portions 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.

[0148] In some embodiments, as shown in Figures 29 and 30, 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 are subjected to the pressure of the liquid in the volume-changing chamber 203. This pressure causes the first shell 107 and the second shell 108 to move away from each other. This pressure is relatively large, making the connection between the first shell 107 and the second shell 108 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, making the docking portion 132 less likely to deform, thereby facilitating the improvement of the connection stability between the first shell 107 and the second shell 108.

[0149] In some embodiments, as shown in FIG27 , the distance L1 from the groove 121 to the wall of the accommodating cavity 101 is greater than or equal to 0.8 mm. This is beneficial for the structure between the groove 121 and the accommodating cavity 101 to have better structural strength and structural rigidity, and is less likely to be damaged or deformed.

[0150] In some embodiments, as shown in FIG28 , 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. This is beneficial for the structure between the groove 121 and the outer surface of the docking portion 132 to have better structural strength and structural rigidity, and is less likely to be damaged or deformed.

[0151] In some embodiments, as shown in Figure 28, 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 prone to damage or deformation.

[0152] In some embodiments, as shown in FIG. 28 , the width w of the protrusion 122 is greater than or equal to 0.8 mm. This helps the protrusion 122 have better structural strength and rigidity and is less likely to be damaged or deformed.

[0153] 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. With this arrangement, the groove 121 is positioned relatively far from the outer surface of the docking portion 132, but relatively close to the accommodating chamber 101. Since the seal 16 is disposed within the groove 121, this prevents a large amount of liquid from entering the gap between the two docking portions 132. Furthermore, when the groove 121 is positioned closer to the accommodating chamber 101, the torque arm generated by the pressure of the liquid within the variable cavity 203 is shortened, thereby further improving the connection stability between the first shell 107 and the second shell 108.

[0154] In some embodiments, as shown in FIG29 , the seal 16 is an annular seal 16. Thus, the seal 16 can be disposed around the accommodating cavity 101, thereby forming a closed sealing structure between the first housing 107 and the second housing 108. Furthermore, the seal 16 has a circular cross-section, which allows the seal 16 to deform significantly when squeezed by the protrusion 122. This allows the seal 16 to more fully fill the space within the groove 121 and maintain close contact with the wall of the groove 121, thereby achieving better sealing performance.

[0155] In some embodiments, as shown in Figures 12, 31, 32, 33, and 34, the driven rotor 202 has a second axis b and is rotatable relative to the pump housing 1 about the second axis b. The driving rotor 201 has a first axis a and is rotatable relative to the pump housing 1 about the first axis a. The driven rotor 202 includes a base 214 and a pin 209 disposed on the base 214. The driving rotor 201 is provided with a groove 210. The pin 209 is constrained within the groove 210 and is rotatable relative to the groove 210 about a third axis c. The pin 209 has a first mating surface 2091 and side surfaces 2092 located on either side of the first mating surface 2091. The first mating surface 2091 connects the two side surfaces 2092. The first mating surface 2091 is an arcuate surface with a central angle less than or equal to 180°. The minimum distance between the two side surfaces 2092 is equal to the chord length d of the first mating surface 2091.

[0156] In this embodiment, the pin portion 209 has a first mating surface 2091 and side surfaces 2092 located on either side of the first mating surface 2091. The first mating surface 2091 is an arcuate surface that mates with the groove 210, thereby constraining the pin portion 2099 within the groove 210 and enabling rotation relative to the groove 210 about the third axis c. Because the first mating surface 2091 is an arcuate surface with a central angle less than or equal to 180°, the first mating surface 2091 does not tend to contract inward near its sides. Furthermore, the minimum distance between the two side surfaces 2092 located on either side of the first mating surface 2091 is equal to the chord length d of the first mating surface 2091, which prevents the two side surfaces 2092 from contracting inward. In this way, the formation of an undercut 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 coordination, thereby reducing the problem of wear caused by interference.

[0157] In some embodiments, referring to FIG34 , both side surfaces 2092 are planar and parallel to each other. Planar side surfaces 2092 facilitate a larger volume of the variable volume cavity 203, thereby increasing the volume of liquid pumped per pump. Furthermore, if the two side surfaces 2092 are parallel to each other, the distance between the two side surfaces 2092 at any position can be adjusted to meet the required distance by simply ensuring that the distance between the two side surfaces 2092 at any position is equal to the chord length of the first mating surface 2091.

[0158] 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.

[0159] 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 denoted as α. When α is greater than 0°, the two side surfaces 2092 are not parallel to each other, but tend to expand outward, which can also avoid the formation of an undercut between the side of the pin shaft portion 209 and the base 214. 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.

[0160] In some embodiments, as shown in Figures 31 and 35 , the groove 210 has a second mating surface 2101 and clearances 2102 located on either side of the second mating surface 2101. The second mating surface 2101 is an arcuate surface, configured to mate with the first mating surface 2091, with a gap between the clearances 2102 and the pin 209. In this embodiment, the groove 210 has the second mating surface 2101, which is an arcuate surface, thereby better matching the first mating surface 2091 of the pin 209. Furthermore, the groove 210 also has clearances 2102 located on either side of the second mating surface 2101, with a gap between the clearances 2102 and the pin 209. During the rotational engagement of the pin and the groove 210, the clearances 2102 serve to prevent interference between the edges of the groove 210 and the pin 209, which could lead to wear.

[0161] Furthermore, the gap between the clearance portion 2102 and the pin portion 209 gradually decreases as it approaches the second mating surface 2101. This arrangement helps to make the surface of the groove 210 smoother and prevent a sudden change at the location of the clearance portion 2102.

[0162] 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 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; conversely, if the gap between the avoidance portion 2102 and the pin shaft portion 209 is too large, particulate matter and impurities will easily enter between the groove 210 and the pin shaft portion 209, which will also lead to increased wear between the driven rotor 202 and the active rotor 201, and even problems such as jamming and damage. 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 better enable the avoidance portion 2102 to play a role in preventing wear, but also better avoid the situation where particulate matter and impurities are easily entered between the groove 210 and the pin shaft portion 209.

[0163] In some embodiments, as shown in Figures 33 and 35, the base portion 214 has two first planar portions 2141 facing the active rotor 201. The two first planar portions 2141 are located on either side of the pin portion 209. The active rotor 201 has two second planar portions 2021 facing the base portion 214. The two second planar portions 2021 are arranged one-to-one opposite the two first planar portions 2141. The pin portion 209, the wall surface of the accommodating cavity 101, the first planar portions 2141, and the corresponding second planar portions 2021 collectively define the variable cavity 203. As the pin portion 209 rotates relative to the groove 210 about the third axis, the volume of the variable cavity 203 changes.

[0164] In this embodiment, the surface of the base 214 facing the driving rotor 201 is formed with two first flat surfaces 2141, and the surface of the driving rotor 201 facing the driven rotor 202 is formed with two second flat surfaces 2021. On this basis, the pin portion 209, the wall of the accommodating cavity 101, the first flat surfaces 2141, and the second flat surfaces 2021 collectively define the variable capacity cavity 203. Compared to curved surfaces, flat surfaces are easier to machine and can achieve higher machining accuracy, thereby facilitating control of the volume of the variable capacity cavity 203.

[0165] In some embodiments, as shown in Figure 31, 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 surface 2101 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 there is a first angle γ 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 there is a second angle θ between the third line and the fourth line, wherein the first angle γ is greater than the second angle θ.

[0166] Such a configuration 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.

[0167] Furthermore, the second angle is less than 40°. If the second angle is too large, then the first angle will also 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 of the pin portion 209 and the groove 210, making the rotor assembly 2 more likely to vibrate and cause noise during rotation.

[0168] In some embodiments, the spherical rotor pump 100 has a first state, in which the volume of one of the two variable-displacement cavities 203 reaches a minimum value, and the volume of the other of the two variable-displacement cavities 203 reaches a maximum value. In the first state, a distance is maintained between the first planar portion 2141 and the corresponding second planar portion 2021 in each variable-displacement cavity 203. This arrangement ensures that the minimum volume of the variable-displacement cavity 203 is greater than zero. In other words, during rotation of the rotor assembly 2, the volume of the variable-displacement cavity 203 is always greater than zero, meaning that the first planar portion 2141 and the second planar portion 2021 never contact each other. This prevents adhesion between the first planar portion 2141 and the second planar portion 2021, which could cause the spherical rotor pump 100 to malfunction.

[0169] In some embodiments, as shown in FIG35 , a transition chamfer 2105 is formed between the clearance portion 2102 and the second planar portion 2021. This configuration allows for a smoother transition between the edge of the groove 210 and the second planar portion 2021, thereby reducing the possibility of interference and wear between the connection between the groove 210 and the second planar portion 2021 and the pin portion 209.

[0170] In some embodiments, the first mating surface 2091 and the second mating surface 2101 are made of materials with the same coefficient of expansion. During rotation of the rotor assembly 2, friction between the first mating surface 2091 of the pin 209 and the second mating surface 2101 of the groove 210 generates heat. Due to thermal expansion and contraction, the structure of the driven rotor 202 at the first mating surface 2091 and the structure of the driving rotor 201 at the second mating surface 2101 expand. The first mating surface 2091 and the second mating surface 2101 are made of materials with the same coefficient of expansion, ensuring consistent expansion. This ensures that the first mating surface 2091 and the second mating surface 2101 maintain a consistent fit, preventing motion jamming caused by poor fit.

[0171] Furthermore, the first mating surface 2091 and the second mating surface 2101 are made of the same material. Thus, the first mating surface 2091 and the second mating surface 2101 must have the same coefficient of expansion, ensuring 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.

[0172] In some embodiments, as shown in FIG33 , the base 214 further comprises an outer surface 2142 that mates with the wall of the accommodating chamber 101 . This outer surface 2142 is spherical. This facilitates smoother rotation of the driven rotor 202 relative to the pump housing 1 . Furthermore, the end surfaces 2095 of the pin 209 along the third axis are spherical surfaces that coincide with the outer surface 2142 . This ensures a good seal between the end surfaces 2095 of the pin 209 and the pump housing 1 , thereby ensuring the sealing performance of the variable capacity chamber 203 .

[0173] In some embodiments, as shown in Figures 39, 40, 41 and 42, the pump housing 1 has a liquid inlet 141 and a liquid outlet 142, and the active rotor 201 or the driven rotor 202 also has a connecting portion 2022 connected to the variable capacity cavity 203, and the connecting portion 2022 is used to periodically connect with the liquid inlet 141 or the liquid outlet 142 during the rotation of the rotor assembly 2.

[0174] In the related art, referring to Figures 37 and 38 , a tooth cleaning device 1000 further includes a housing 200, a liquid reservoir 400, and a nozzle 300. The housing 200 is disposed over the spherical rotor pump 100 and the liquid reservoir 400 to protect them and reduce the likelihood of damage to them, thereby extending the service life of the spherical rotor pump 100 and the liquid reservoir 400 and, consequently, the tooth cleaning device 1000. The spherical rotor pump 100 is disposed within the housing 200 and connects the liquid reservoir 400 to the nozzle 300 via a pipeline, thereby pumping liquid from the liquid reservoir 400 to the nozzle 300 to clean the user's oral cavity. The liquid reservoir 400 is disposed within the housing 200 to store liquid, which may include at least one of a cleaning solution and water. The nozzle 300 extends outside the body shell 200 so that the spherical rotor pump 100 can pump the liquid in the liquid storage tank 400 to the nozzle 300 and spray it out through the nozzle 300, thereby achieving the purpose of cleaning the user's oral cavity.

[0175] The active rotor 201 or the driven rotor 202 further has a communication portion 2022 communicating with the variable capacity cavity 203 . The communication portion 2022 is used to periodically communicate with the liquid inlet 141 or the liquid outlet 142 during the rotation of the rotor assembly 2 . When the extrusion force exerted by the active rotor 201 and the driven rotor 202 on the liquid is at its maximum, and the variable cavity 203 is connected to the liquid outlet 142 via the connecting portion 2022, the variable cavity 203 can pump liquid to the nozzle 300 via the connecting portion 2022 and the liquid outlet 142, thereby ensuring that the pressure of the liquid ejected from the nozzle 300 is high, thereby ensuring a better cleaning effect on the user's oral cavity. Furthermore, when the extrusion force exerted by the active rotor 201 and the driven rotor 202 on the liquid is low, the connecting portion 2022 and the liquid outlet 142 are offset, and the liquid in the variable cavity 203 is not pumped to the nozzle 300, thereby reducing the amount of liquid discharged from the nozzle 300, thereby reducing the use of liquid in the liquid storage tank 400, thereby increasing the user's usage time and improving the cleaning effect. Furthermore, the less liquid used in the liquid storage tank 400 can reduce the volume of the liquid storage tank 400, thereby reducing the overall volume of the teeth cleaning device 1000, making it easier for the user to carry and use the teeth cleaning device 1000.

[0176] In some embodiments, as shown in Figures 41, 42 and 43, the spherical rotor pump 100 further includes a transmission shaft 3 connected to the driving rotor 201. The pump housing 1 includes a first housing 107 and a second housing 108. The first housing 107 has a liquid inlet 141 and a liquid outlet 142. The driven rotor 202 is at least partially disposed within the first housing 107 and is rotationally connected to the first housing 107. The second housing 108 is connected to the first housing 107. The driving rotor 201 is disposed within the second housing 108. The transmission shaft 3 extends from the driving rotor 201 to the outside of the second housing 108 so that the driving rotor 201 is rotationally connected to the second housing 108. The liquid inlet 141 and the liquid outlet 142 are both arranged on the first shell 107, and the transmission shaft 3 passes through the second shell 108 and is connected to the active rotor 201, so that the transmission shaft 3 and the liquid inlet 141 and the liquid outlet 142 can be respectively arranged on both sides of the pump housing 1, so as to reduce the influence of the transmission shaft 3 on the connecting pipeline of the liquid inlet 141 and the connecting pipeline of the liquid outlet 142, thereby improving the connection stability between the pipeline and the liquid inlet 141 and the pipeline and the liquid outlet 142, thereby ensuring that the spherical rotor pump 100 can pump the liquid in the liquid storage tank 400 to the nozzle 300, and spray it through the nozzle 300 to clean the user's mouth.

[0177] In one embodiment, as shown in Figures 41 and 42, the driven rotor 202 has a bottom surface 2023 facing the driving rotor 201, and the bottom surface 2023 constitutes part of the cavity wall of the variable cavity 203. The driven rotor 2022 also has a spherical surface 2024 connected to the bottom surface 2023 and arranged away from the variable cavity 203. The connecting portion 2022 can be a through hole with two ends respectively penetrating the bottom surface 2023 and the spherical surface 2024. When the squeezing force of the driving rotor 201 and the driven rotor 202 on the liquid is maximum, the through hole is connected to the liquid outlet 142, and the liquid in the variable cavity 203 can be pumped to the nozzle 300 through the through hole and the liquid outlet 142 to clean the user's mouth.

[0178] It can be understood that the connecting portion 2022 can also be a notch provided at the connection between the bottom surface 2023 and the spherical surface 2024. Similarly, when the squeezing force of the active rotor 201 and the driven rotor 202 on the liquid is maximum, the notch is connected to the liquid outlet 142, and the liquid in the variable volume cavity 203 can be pumped to the nozzle 300 through the notch and the liquid outlet 142 to clean the user's mouth.

[0179] In one embodiment, along the rotational direction of the driven rotor 202, the gap has a first circumferential length, and the variable cavity 203 has a second circumferential length, and the first circumferential length is not greater than 1 / 2 of the second circumferential length, so that when the active rotor 201 drives the driven rotor 202 to rotate, the time in which the gap is connected to the liquid outlet 142 is shorter, thereby reducing the amount of liquid output from the nozzle 300, thereby reducing the use of liquid in the liquid storage tank 400, making the liquid storage tank 400 smaller, and thus making the volume of the tooth cleaning device 1000 smaller, which is convenient for carrying and using the tooth cleaning device 1000; and ensuring that the liquid sprayed out through the nozzle 300 has a higher pressure, so as to improve the cleaning effect on the user's mouth.

[0180] If the first circumferential length is greater than 1 / 2 of the second circumferential length, the size of the gap will be larger, and when the active rotor 201 drives the driven rotor 202 to rotate, the gap will be connected to the liquid outlet 142 for a longer time, resulting in a larger amount of liquid output from the nozzle 300, resulting in more liquid in the liquid storage tank 400 used, and the required volume of the liquid storage tank 400 is larger, resulting in a larger liquid storage tank 400, resulting in a larger volume of the tooth cleaning device 1000, which is inconvenient to carry and use the tooth cleaning device 1000; and because the gap is connected to the liquid outlet 142 for a long time, the pressure sprayed by the nozzle 300 will gradually decrease, resulting in a poor cleaning effect on the user's oral cavity.

[0181] In one embodiment, along the rotation axis of the driven rotor 202, the gap has a first axial thickness, the variable cavity 203 has a second axial thickness, and the first axial thickness is not greater than 1 / 2 of the second axial thickness; so that when the active rotor 201 drives the driven rotor 202 to rotate, the gap is smaller, thereby reducing the liquid output of the nozzle 300, thereby reducing the use of liquid in the liquid storage tank 400, and making the liquid storage tank 400 smaller, thereby making the volume of the tooth cleaning device 1000 smaller, which is convenient for carrying and using the tooth cleaning device 1000; and ensuring that the liquid sprayed out through the nozzle 300 has a higher pressure, so as to improve the cleaning effect on the user's mouth.

[0182] If the first axial thickness is greater than 1 / 2 of the second axial thickness; the size of the gap is larger, resulting in a larger liquid output from the nozzle 300 when the active rotor 201 drives the driven rotor 202 to rotate, resulting in more liquid in the liquid storage tank 400 used, and the required volume of the liquid storage tank 400 is larger, resulting in a larger liquid storage tank 400, resulting in a larger volume of the tooth cleaning device 1000, which is inconvenient to carry and use the tooth cleaning device 1000; and due to the larger gap, the pressure sprayed by the nozzle 300 will be smaller, resulting in a poor cleaning effect on the user's oral cavity.

[0183] In one embodiment, the notch is formed with a bottom opening on the bottom surface 2023, and the depth of the bottom opening does not exceed the rotational connection between the driven rotor 202 and the active rotor 201. Similarly, when the active rotor 201 drives the driven rotor 202 to rotate, the amount of liquid discharged from the nozzle 300 is small, so as to reduce the use of liquid in the liquid storage tank 400, and the liquid storage tank 400 can be made smaller, thereby making the volume of the tooth cleaning device 1000 smaller, making it easier to carry and use the tooth cleaning device 1000.

[0184] In some embodiments, as shown in Figure 41, the number of the variable-capacity chambers 203 is two, the number of the connecting parts 2022 is two, and the connecting parts 2022 are arranged in a one-to-one correspondence with the variable-capacity chambers 203, so that in the process of the active rotor 201 driving the driven rotor 202 to rotate 180°, there is a variable-capacity chamber 203 connected to the liquid outlet 142 through the connecting part 2022, so that the liquid in the variable-capacity chamber 203 can be pumped out, which can improve the liquid discharge efficiency of the spherical rotor pump 100, and then improve the liquid discharge efficiency of the nozzle 300, so as to improve the cleaning efficiency of the tooth cleaning device 1000 on the user's oral cavity.

[0185] Furthermore, along the rotational circumference of the driven rotor 202, the connecting portion 2022 is located in the middle of the variable cavity 203 connected to the connecting portion 2022. Compared with setting the connecting portion 2022 on one side of the variable cavity 203, the water outlet pressure of the liquid outlet 142 can be greater, thereby improving the cleaning effect of the tooth cleaning device 1000 on the user's oral cavity.

[0186] Furthermore, the two connecting portions 2022 can be centrally symmetrically arranged about the rotation axis of the driven rotor 202, so that the water outlet pressure of the liquid outlet 142 can be higher, thereby improving the cleaning effect of the tooth cleaning device 1000 on the user's oral cavity.

[0187] In some embodiments, the rotating shaft of the driven rotor 202, the liquid inlet 141 and the liquid outlet 142 are cross-sectioned by the same reference plane, so that the flow rate entering the variable cavity 203 through the liquid inlet 141 is larger, and the pressure of the liquid flowing out of the variable cavity 203 to the nozzle 300 through the liquid outlet 142 is larger, thereby improving the water pumping efficiency of the spherical rotor pump 100 and improving the cleaning effect of the tooth cleaning device 1000 on the user's mouth.

[0188] In some embodiments, since the liquid in the variable cavity 203 will be pumped out through the liquid outlet 142 only when the connecting portion 2022 is connected to the liquid outlet 142, the inner wall surface of the first shell 107 has a liquid inlet channel 146 connected to the liquid inlet 141. When the liquid inlet channel 146 is connected to the variable cavity 203, the connecting portion 2022 is not connected to the liquid outlet 142. When the liquid inlet channel 146 is not connected to the variable cavity 203, the connecting portion 2022 is connected to the liquid outlet 142, so that when the active rotor 201 and the driven rotor 202 exert a small extrusion force on the liquid, and the connecting portion 2022 is staggered from the liquid outlet 142, the liquid in the variable cavity 203 can flow to the liquid inlet 141 through the liquid inlet channel 146, so that the volume of the variable cavity 203 can continuously change, thereby facilitating the active rotor 201 to drive the driven rotor 202 to move, so as to pump out the liquid in the liquid storage tank 400 and clean the user's mouth.

[0189] In some embodiments, as shown in Figure 43, the inner wall surface of the first shell 107 has a liquid outlet channel 147 connected to the liquid outlet 142. When the liquid inlet channel 146 is connected to the variable cavity 203, the connecting portion 2022 is not connected to the liquid outlet channel 147. When the liquid inlet channel 146 is not connected to the variable cavity 203, the connecting portion 2022 is connected to the liquid outlet channel 147. The liquid outlet channel 147 facilitates the liquid in the variable cavity 203 to enter the liquid inlet 141 through the connecting portion 2022, and then facilitates the liquid to be sprayed out through the nozzle 300 to clean the user's mouth.

[0190] Exemplarily, within a single rotation cycle of 180°, the driven rotor 202 has a first rotation angle α and a second rotation angle β. Within the first rotation angle α, the liquid inlet channel 146 is always connected to the variable volume chamber 203, and within the second rotation angle β, the connecting portion 2022 is always connected to the liquid outlet channel 147, and the sum of the first rotation angle α and the second rotation angle β is equal to 180°, so that when the active rotor 201 and the driven rotor 202 exert a small squeezing force on the liquid, and the connecting portion 2022 is staggered with the liquid outlet 142, the liquid in the variable volume chamber 203 can flow to the liquid inlet 141 through the liquid inlet channel 146, so that the volume of the variable volume chamber 203 continues to change, thereby facilitating the active rotor 201 to drive the driven rotor 202 to move, and further facilitating the spherical rotor pump 100 to pump the liquid in the liquid storage tank 400 to the nozzle 300, so as to clean the user's mouth.

[0191] In one embodiment, as shown in Figures 41 and 43 , the liquid inlet channel 146 is an arcuate channel located on the inner wall of the first housing 107. The arcuate channel is formed by a recess in the inner wall of the first housing 107. In other embodiments, the liquid inlet channel 146 can also have other forms. In the embodiments of the present application, the specific form of the liquid inlet channel 146 is not limited.

[0192] Furthermore, the arc channel is extended along the rotation circumference of the driven rotor 202, and the arc channel includes a first arc segment 1461 and a second arc segment 1462 located on both sides of the liquid inlet 141. The first arc segment 1461 and the second arc segment 1462 are axially symmetrical about the liquid inlet 141, so that before the connecting portion 2022 is connected to the liquid outlet 142, the liquid in the variable cavity 203 can flow back to the liquid inlet 141 through the first arc segment 1461; after the connecting portion 2022 is connected to the liquid outlet 142, the liquid in the variable cavity 203 can flow back to the liquid inlet 141 through the second arc segment 1462, so that the volume of the variable cavity 203 changes, thereby facilitating the spherical rotor pump 100 to pump the liquid in the liquid storage tank 400 to the nozzle 300, so as to clean the user's mouth.

[0193] In some embodiments, as shown in Figure 44, the number of the connecting portion 2022 can be one, the active rotor 201 has a pressure relief groove 2025 connected to the liquid inlet 141, and the number of the variable cavity 203 is two, one of the variable cavity 203 is connected to the connecting portion 2022, and the other variable cavity 203 is connected to the pressure relief groove 2025.

[0194] Specifically, the two variable-volume chambers 203 are respectively a first variable-volume chamber and a second variable-volume chamber. The first variable-volume chamber is connected to the connecting portion 2022, while the second variable-volume chamber is connected to the liquid inlet 141 via the pressure relief groove 2025. This allows the first variable-volume chamber to pump liquid to the nozzle 300, further reducing the use of liquid in the liquid reservoir 400 and the volume of the liquid reservoir 400, thereby reducing the size of the tooth cleaning device 1000 and facilitating its use and portability. Furthermore, when the volume of the first variable-volume chamber is reduced and the connecting portion 2022 is offset from the liquid outlet 142, the liquid in the first variable-volume chamber can flow through the liquid inlet channel 146 to the second variable-volume chamber and then flow back to the liquid inlet 141 via the pressure relief groove 2025, ensuring that the driving rotor 201 can drive the driven rotor 202 to move, thereby pumping the liquid in the liquid reservoir 400 to the nozzle 300, thereby cleaning the user's oral cavity.

[0195] In some embodiments, as shown in Figures 39 and 40, the first housing 107 includes a first housing body 1071, a liquid inlet pipe 148, and a liquid outlet pipe 149. The first housing body 1071 has a liquid inlet 141 and a liquid outlet 142. The driven rotor 202 is at least partially disposed within the first housing body 107 and is rotatably connected to the first housing body 1071. The liquid inlet pipe 148 is connected to the first housing body 1071 and communicates with the liquid inlet 141. The liquid outlet pipe 149 is connected to the first housing body 1071 and communicates with the liquid outlet 142. The liquid inlet pipe 148 and the liquid outlet pipe 149 are arranged on both sides of the first shell body 1071 and are arranged at an angle, so as to facilitate the communication between the liquid inlet pipe 148 and the liquid storage tank 400, and also facilitate the communication between the liquid outlet pipe 149 and the nozzle 300. It can also reduce the probability of interference between the liquid inlet pipe and the liquid outlet pipe, so as to improve the installation stability of the liquid inlet pipe and the liquid outlet pipe, and ensure that the spherical rotor pump 100 can pump the liquid in the liquid storage tank 400 to the nozzle 300, and spray it through the nozzle 300 to clean the user's mouth.

[0196] In some embodiments, as shown in Figures 41 and 42, the pump housing 1 further has a positioning groove 143, which is arranged on a side of the pump housing 1 away from the transmission shaft 3, and a limiting portion 2027 is provided on the outer peripheral side of the driven rotor 202; the spherical rotor pump 100 further includes a limiting shaft 28, which is rotatably arranged in the positioning groove 143, and the axis of the limiting shaft 28 is arranged at an angle to the axis of the transmission shaft 3. The limiting shaft 28 has a limiting groove 281, the notch of the limiting groove 281 is arranged toward the driven rotor 202, and the limiting portion 2027 is slidably arranged in the limiting groove 281; wherein, the active rotor 201 drives the driven rotor 202 to rotate, so that the limiting shaft 28 rotates in the positioning groove 143, and the limiting portion 2027 moves along the limiting groove 281, so that the volume of the variable cavity 203 increases or decreases, and then the liquid in the liquid storage tank 400 can be pumped out through the nozzle 300 to clean the user's mouth.

[0197] In some embodiments, as shown in FIG42 , the side of the driven rotor 202 facing the active rotor 201 has a first curved surface 2026, and the side of the active rotor 201 facing the driven rotor 202 has a second curved surface 2011. The first curved surface 2026 and the second curved surface 2011 cooperate in a concave-convex manner to achieve a rotational connection between the active rotor 201 and the driven rotor 202, thereby facilitating the rotation of the driven rotor 202 relative to the active rotor 201, causing the volume of the variable volume chamber 203 to change, thereby allowing the liquid to be pumped to the nozzle 300 through the liquid outlet 142 and sprayed through the nozzle 300 to clean the user's oral cavity. In other embodiments, the spherical rotor pump 100 further includes a rotating shaft 27, which connects the active rotor 201 and the driven rotor 202. The active rotor 201 drives the driven rotor 202 to rotate via the rotating shaft 27. In the embodiments of the present application, the specific connection method between the active rotor 201 and the driven rotor 202 is not limited.

[0198] In some embodiments, as shown in Figures 40 and 41, in order to facilitate the rotation of the active rotor 201, the spherical rotor pump 100 further includes a transmission shaft 3 and a driving device 5. The transmission shaft 3 passes through the pump housing 1 and is fixedly connected to the active rotor 201. The driving device 5 is in transmission connection with the transmission shaft 3 and is electrically connected to the main control board so that the main control board controls the action of the driving device 5 so that the driving device 5 can drive the transmission shaft 3 to drive the active rotor 201 to rotate, thereby pumping the liquid in the liquid storage tank 400 to the nozzle 300 and spraying it through the nozzle 300 to clean the user's mouth.

[0199] Specifically, as shown in Figure 40, the spherical rotor pump 100 also includes a bevel gear 25 and a gear plate 26. The bevel gear 25 is engaged with the output shaft 501 of the driving device 5, and the gear plate 26 is engaged with the bevel gear 25. It is connected to the transmission shaft 3 and is coaxially arranged. By utilizing the engagement of the bevel gear 25 and the gear plate 26, the axis of the output shaft 501 of the driving device 5 can be set at an angle to the axis of the transmission shaft 3, thereby reducing the space occupied inside the body shell 200 along the axial direction of the transmission shaft 3, thereby reducing the size of the body shell 200 along the axial direction of the transmission shaft 3, thereby reducing the volume of the tooth cleaning device 1000, so as to facilitate the use and carrying of the tooth cleaning device 1000.

[0200] The second embodiment of the present application provides a teeth cleaning device 1000, comprising the spherical rotor pump 100 of any of the aforementioned embodiments. As shown in FIG36 , the teeth cleaning device 1000 may include a housing 200, a nozzle 300 disposed on the housing 200, and the spherical rotor pump 100 for delivering liquid to the nozzle 300.

[0201] In the tooth cleaning device 1000 of the embodiment of the present application, the housing of the spherical rotor pump 100 has a housing chamber 101 and a mounting chamber 102, the housing chamber 101 and the mounting chamber 102 being 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 the gap seal between the rotor assembly 2 and the inner wall of the housing chamber 101 fails, the risk of liquid overflowing from the transmission shaft 3 can be reduced.

[0202] The same or similar numbers in the drawings of this embodiment correspond to the same or similar parts; in the description of this application, it should be understood that if the terms "upper", "lower", "left", "right", etc. indicate an orientation or position relationship, they are based on the orientation or position relationship shown in the drawings. This is only for the convenience of describing this 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 operate in a specific orientation. Therefore, the terms describing the position 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.

[0203] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application should be included in the scope of protection of the present application.

Claims

1. A spherical rotor pump, wherein: include: A pump housing, the pump housing having an accommodating cavity and an installation cavity, the accommodating cavity and the installation cavity being separated by a partition plate, and the partition plate being provided with a through hole; A rotor assembly, the rotor assembly comprising a driving rotor and a driven rotor, the driving rotor and the driven rotor both being located within the accommodating cavity, the driving rotor, the driven rotor, and the wall of the accommodating cavity jointly defining a variable capacity cavity, the driving rotor being capable of driving the driven rotor to rotate, and when the driving rotor drives the driven rotor to rotate, the volume of the variable capacity cavity changes; a transmission shaft, the transmission shaft passing through the through hole, a portion of the transmission shaft being located in the mounting cavity, and another portion of the transmission shaft extending into the accommodating cavity and connected to the active rotor; and A 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.

2. The spherical rotor pump according to claim 1, wherein: 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, wherein: The spherical rotor pump also includes: A bearing, the bearing being located in the installation cavity, the bearing being sleeved on the transmission shaft, the bearing being arranged on a side of the sealing ring away from the partition, and the bearing being in contact with a wall surface of the installation cavity; and An isolation member is located between the bearing and the sealing ring.

4. The spherical rotor pump according to claim 3, wherein: The installation cavity includes a first section and a second section that communicate with 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 greater 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, and 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, wherein: 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 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.

6. The spherical rotor pump according to claim 3, wherein: 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, wherein: 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 bearing inner ring. A relief gap is formed on the side of the gasket close to the bearing, and the relief gap is arranged opposite to the bearing inner ring to avoid the bearing inner ring.

8. The spherical rotor pump according to claim 1, wherein: 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, wherein: A first placement groove is provided in the accommodating cavity, and the sealing ring is located in the first placement groove.

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

11. The spherical rotor pump according to claim 10, wherein: 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, wherein: The thickness of the anti-wear pad is greater than the depth of the second placement groove, so that a portion of the structure of the anti-wear pad extends out of the second placement groove.

13. The spherical rotor pump according to claim 11, wherein 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 active rotor close to the anti-wear pad. The limiting end surface is a plane and abuts against the anti-wear pad.

14. The spherical rotor pump according to claim 13, wherein: A limiting portion is formed at one end of the driving rotor away from the driven rotor, and the limiting end surface is formed on the limiting portion; A third placement groove is further 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, wherein The anti-wear pad 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, wherein The sealing ring is a Y-shaped sealing ring, which includes a sealing ring body. One side of the sealing ring body is provided with an inner lip and an outer lip, and the inner lip and the outer lip are against the partition.

17. The spherical rotor pump according to claim 1, wherein 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 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 includes a bearing, which is located in the installation cavity, is sleeved on the transmission shaft and / or the output shaft, is arranged on a side of the sealing ring away from the partition, and is in contact with a wall surface of the installation cavity; The spherical rotor pump further includes a support block, which is arranged on a side of the bearing away from the partition plate, and is fixed in the installation cavity.

18. The spherical rotor pump according to claim 17, wherein: 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 mounting 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, wherein: The active rotor includes a first support member and a first encapsulated body, wherein the first support member is wrapped 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 encapsulated body, and the second encapsulated body covers at least a portion of the second support member.

20. The spherical rotor pump according to claim 1, wherein The spherical rotor pump further includes a limiting structure, which is provided between the transmission shaft and the pump housing. The limiting structure is used to limit the movement of the transmission shaft relative to the pump housing along its own axis.

21. The spherical rotor pump according to claim 20, wherein: The pump casing 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 casing. 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, wherein 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.

23. The spherical rotor pump according to claim 22, wherein: 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, wherein: 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, wherein 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, wherein The second component is a snap ring, and the snap ring is interference-fitted with the installation cavity.

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

28. The spherical rotor pump according to claim 27, wherein The active rotor includes a first support member and a first encapsulated body, wherein a portion of the first support member is encapsulated within the first encapsulated body to serve as an inner skeleton of the active rotor, and another portion 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, wherein 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, wherein The driving rotor has a first axis, the driving rotor is rotatable relative to the pump housing about the first axis, the driven rotor has a second axis, the driven rotor is rotatable relative to the pump housing about the second axis, and the first axis intersects the second axis; The driven rotor is provided with a groove, and 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, wherein The spherical rotor pump further includes 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 restraint 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, wherein The output shaft and the restraint 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, wherein The output shaft and the restraint structure are both located in the mounting cavity, a portion of the transmission shaft is located in the mounting cavity, and another portion of the transmission shaft extends into the accommodating cavity; The constraint structure is a bearing, which is located in the installation cavity, and the outer wall surface of the bearing contacts the wall surface of the installation cavity.

34. The spherical rotor pump according to claim 33, wherein: The driving device further includes 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 includes a support block. The support block 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, wherein The output shaft includes a first mating portion, which is provided with a first contact surface. The transmission shaft includes a second mating portion, which is provided with a second contact surface. The first contact surface and the second contact surface are tightly abutted against each other so that torque can be transmitted between the output shaft and the transmission shaft.

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

37. The spherical rotor pump according to claim 35, wherein 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, wherein The output shaft includes a third mating portion, and the transmission shaft includes a fourth mating portion. One of the third mating portion and the fourth mating portion is a prismatic structure, and the other of the third mating portion and the fourth mating 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 is matched with the inner cavity.

39. The spherical rotor pump according to claim 31, wherein 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, which 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, wherein 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, wherein The spherical rotor pump further includes a sealing member; The pump housing includes a first shell and a second shell connected to the first shell, the first shell and the second shell together 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, wherein The thickness of the protrusion gradually decreases in a direction away from the rotor assembly.

43. The spherical rotor pump according to claim 42, wherein: 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, wherein 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 is rotatable relative to the pump housing about the second axis, and the first axis intersects the second axis; The end surface of the protrusion is perpendicular to the second axis, or the angle between the end surface 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, wherein 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.

46. The spherical rotor pump according to claim 41, wherein 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, wherein The docking portion of the first shell and / or the docking portion of the second shell are provided with reinforcing ribs.

48. The spherical rotor pump according to claim 46, wherein The distance between the groove and the wall of the accommodating cavity is greater than or equal to 0.8 mm; and / or, a distance from the groove to the outer surface of the docking portion is greater than or equal to 0.8 mm; and / or, a distance from the bottom of the groove to the surface of the butting portion 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, wherein 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, wherein The sealing member is an annular sealing member, and the cross-section of the sealing member is circular.

51. The spherical rotor pump according to claim 1, wherein The driven rotor has a second axis, and the driven rotor is rotatable relative to the pump housing about the second axis; The driving rotor has a first axis and is rotatable relative to the pump housing about the first axis. The driven rotor includes a base and a pin portion provided on the base. A groove is provided on the driving rotor. The pin portion is constrained in the groove and is rotatable relative to the groove about 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-shaped surface and the central angle 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.

52. The spherical rotor pump according to claim 51, wherein 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, wherein 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, wherein 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 used to cooperate with the first mating surface. There is a gap between the avoidance portion and the pin shaft portion.

55. The spherical rotor pump according to claim 54, wherein 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, wherein 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, wherein The base has two first flat surfaces facing the active rotor, the two first flat surfaces are located on both sides of the pin shaft, and the active rotor has two second flat surfaces facing the base, the two second flat surfaces are arranged opposite to the two first flat surfaces 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, wherein An end of the avoidance portion away from the second mating surface is a first end, an end of the 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, wherein The second angle is smaller than 40°.

60. The spherical rotor pump according to claim 57, wherein The spherical rotor pump has a first state, in which the volume of one of the two variable-volume cavities reaches a minimum value, and the volume of the other of the two variable-volume cavities reaches a maximum value; In the first state, a distance is maintained between the first plane portion and the corresponding second plane portion in any variable-capacity cavity.

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

62. The spherical rotor pump according to claim 54, wherein 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, wherein: The first mating surface and the second mating surface are made of the same material.

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

65. The spherical rotor pump according to claim 1, wherein The pump housing has a liquid inlet and a liquid outlet, and the active rotor or the driven rotor also has a connecting portion connected to the variable capacity cavity, and the connecting portion is used to periodically connect with the liquid inlet or the liquid outlet during the rotation of the rotor assembly.

66. The spherical rotor pump according to claim 65, wherein The spherical rotor pump further includes a transmission shaft connected to the active rotor, and the pump housing includes: a first housing having the liquid inlet and the liquid outlet, wherein the driven rotor is at least partially disposed in the first housing and is rotatably connected to the first housing; and The second housing is connected to the first housing. The driving rotor is disposed in the second housing. The transmission shaft extends from the driving rotor to the outside of the second housing so that the driving rotor is rotatably connected to the second housing.

67. The spherical rotor pump according to claim 66, wherein The driven rotor has a bottom surface facing the driving rotor, the bottom surface forming part of the cavity wall of the variable capacity cavity, and the driven rotor further has a spherical surface connected to the bottom surface and disposed away from the variable capacity cavity; The connecting portion is a through hole with two ends passing through the bottom surface and the spherical surface respectively, or the connecting portion is a notch provided at the connection between the bottom surface and the spherical surface.

68. The spherical rotor pump according to claim 67, wherein The connecting portion is a notch provided at the connection between the bottom surface and the spherical surface, wherein the notch satisfies one of the following conditions: Along the rotational circumference of the driven rotor, the notch has a first circumferential length, the variable capacity cavity has a second circumferential length, and the first circumferential length is no greater than 1 / 2 of the second circumferential length; Along the rotational axis of the driven rotor, the notch has a first axial thickness, the variable capacity cavity has a second axial thickness, and the first axial thickness is no greater than 1 / 2 of the second axial thickness; The notch forms a bottom opening on the bottom surface, and the depth of the bottom opening does not exceed the rotation connection between the driven rotor and the driving rotor.

69. The spherical rotor pump according to claim 66, wherein The number of the variable-capacity cavities is two, the number of the communicating portions is two, and the communicating portions are arranged in a one-to-one correspondence with the variable-capacity cavities.

70. The spherical rotor pump according to claim 69, wherein Along the rotational circumference of the driven rotor, the communication portion is located in the middle of the variable capacity cavity communicated with the communication portion; and / or, The two communication portions are centrally symmetrically arranged with respect to the rotation axis of the driven rotor.

71. The spherical rotor pump according to claim 70, wherein The rotating shaft of the driven rotor, the liquid inlet, and the liquid outlet are cross-sectioned by the same reference plane.

72. The spherical rotor pump according to claim 66, wherein The inner wall surface of the first shell has a liquid inlet channel connected to the liquid inlet. When the liquid inlet channel is connected to the variable capacity cavity, the communicating portion is not connected to the liquid outlet. When the liquid inlet channel is not connected to the variable capacity cavity, the communicating portion is connected to the liquid outlet.

73. The spherical rotor pump according to claim 72, wherein: The inner wall surface of the first shell has a liquid outlet channel connected to the liquid outlet. When the liquid inlet channel is connected to the variable volume cavity, the communicating portion is not connected to the liquid outlet channel. When the liquid inlet channel is not connected to the variable volume cavity, the communicating portion is connected to the liquid outlet channel.

74. The spherical rotor pump according to claim 73, wherein: Within a single rotation cycle of 180°, the driven rotor has a first rotation angle α and a second rotation angle β. Within the first rotation angle α, the liquid inlet channel is always connected to the variable volume cavity. Within the second rotation angle β, the connecting portion is always connected to the liquid outlet channel, and the sum of the first rotation angle α and the second rotation angle β is equal to 180°.

75. The spherical rotor pump according to claim 72, wherein: The liquid inlet channel is an arc-shaped channel located on the inner wall surface of the first shell, and the arc-shaped channel is formed by a depression in the inner wall surface of the first shell.

76. The spherical rotor pump according to claim 75, wherein The arcuate channel extends along the rotational circumference of the driven rotor, and includes a first arcuate segment and a second arcuate segment located on both sides of the liquid inlet. The first arcuate segment and the second arcuate segment are axially symmetrically arranged about the liquid inlet.

77. The spherical rotor pump according to claim 65, wherein The number of the communication part is one, the active rotor has a pressure relief groove connected to the liquid inlet, the number of the variable capacity chamber is two, one of the variable capacity chambers is connected to the communication part, and the other of the variable capacity chambers is connected to the pressure relief groove.

78. The spherical rotor pump according to claim 66, wherein The first housing comprises: a first shell body having the liquid inlet and the liquid outlet, wherein the driven rotor is at least partially disposed in the first shell body and is rotatably connected to the first shell body; a liquid inlet pipe connected to the first shell body and communicated with the liquid inlet; and a liquid outlet pipe connected to the first shell body and communicated with the liquid outlet; The liquid inlet pipe and the liquid outlet pipe are respectively arranged on both sides of the first shell body and are arranged at an angle.

79. The spherical rotor pump according to claim 65, wherein The driven rotor has a first curved surface on a side facing the driving rotor, and the driving rotor has a second curved surface on a side facing the driven rotor, and the first curved surface and the second curved surface are matched in a concave-convex manner; or, The spherical rotor pump further includes a rotating shaft, wherein the rotating shaft connects the driving rotor and the driven rotor, and the driving rotor drives the driven rotor to rotate via the rotating shaft.

80. The spherical rotor pump according to any one of claims 65 to 79, wherein: The spherical rotor pump also includes: A transmission shaft passing through the pump housing and fixedly connected to the driving rotor; A driving device, drivingly connected to the transmission shaft; a bevel gear meshing with the output shaft of the drive device; and The gear plate is engaged with the bevel gear and is connected to the transmission shaft and is coaxially arranged.

81. The spherical rotor pump according to claim 80, wherein The pump housing further comprises a positioning groove, which is arranged on a side of the pump housing away from the transmission shaft, and a limiting portion is arranged on the outer peripheral side of the driven rotor; The spherical rotor pump also includes: a limiting shaft rotatably disposed in the positioning groove, wherein the axis of the limiting shaft is disposed at an angle to the axis of the transmission shaft, the limiting shaft has a limiting groove, the notch of the limiting groove is disposed toward the driven rotor, and the limiting portion is slidably disposed in the limiting groove; The active rotor drives the driven rotor to rotate, so that the limiting shaft rotates in the positioning groove, and the limiting portion moves along the limiting groove, so that the volume of the variable capacity cavity increases or decreases.

82. A tooth cleaning device, wherein: A spherical rotor pump comprising the spherical rotor pump according to any one of claims 1 to 81.

Images