Fluid pumping unit and oral cavity cleaning appliance

Abstract

Provided are a fluid pumping unit and an oral cavity cleaning appliance comprising a housing, a displacement unit, and a linkage unit. The displacement unit is movably arranged in the housing, and the end face of the displacement unit toward the first direction and the inner wall of the housing define, in an enclosing manner, a fluid pump cavity with a variable volume. The linkage unit is arranged in the shell and connected with the end face of the displacement unit toward the second direction, and the linkage unit is suitable for driving the displacement unit to reciprocate in the first direction and the second direction so as to cyclically increase and reduce the volume of the fluid pump cavity, so that liquid in the container is pumped into the fluid pump cavity through a fluid input channel and pumped out through a fluid output channel to provide an impact fluid, wherein two extreme positions are present during the reciprocating movement process of the displacement unit in the first direction and the second direction; the distance between the two extreme positions ranges from 2.1 mm to 2.6 mm, and the volume of the liquid pumping cavity ranges from 120 mm 3 to 165 mm 3.

Description

Fluid pumping unit and oral cleaning device

[0001] Cross-references

[0002] This application claims priority to Chinese Patent Application No. 2023118671283, filed on December 29, 2023, entitled “Fluid Pumping Unit and Oral Cleaning Appliance” and Chinese Patent Application No. 2023118699077, filed on December 29, 2023, entitled “Oral Cleaning Appliance”. The entire contents of the Chinese patent applications are incorporated into this application by reference. Technical Field

[0003] The present invention relates to the technical field of oral cleaning appliances, and in particular to a fluid pumping unit and an oral cleaning appliance. Background Art

[0004] A water flosser is a commonly used oral care device. Its general structure consists of a nozzle and a handle. The handle houses a pump body connected to the nozzle and a water tank. During use, the pump body pumps water from the water tank, pressurizing the water through the pump body and internal reducing pipes. The water then sprays out of the nozzle, cleaning the user's teeth.

[0005] To ensure cleaning power, conventional water flossers in the prior art generally use larger pumps that consume more water. To meet the water requirements of the pump, the water tank must be increased in size, which results in an oversized handle and a reduced user experience. A conventional improvement involves reducing the volume of the water tank while maintaining the pump volume. While this reduces the size of the handle to a certain extent, it also affects the water output of the nozzle, which in turn reduces cleaning power and affects the cleaning effect. Therefore, conventional water flossers fail to resolve the conflict between product size and cleaning power.

[0006] Summary of the Invention

[0007] In view of this, the present invention provides a fluid pumping unit and an oral cleaning device to solve the problem of the contradiction between product size and cleaning power of the oral irrigator in the prior art.

[0008] In a first aspect, the present invention provides a fluid pumping unit for an oral cleaning appliance, comprising: a shell, in which a fluid pump chamber is formed, and a fluid input channel and a fluid output channel connected to the fluid pump chamber; a displacement unit movably arranged in the shell, wherein the end face of the displacement unit facing the first direction is enclosed and sealed with the inner wall of the shell to form the fluid pump chamber with a variable volume; a linkage unit, arranged in the shell and transmission-connected to the end face of the displacement unit facing the second direction, the linkage unit being suitable for driving the displacement unit to reciprocate along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber, so that the liquid in the fluid storage unit is pumped into the fluid pump chamber through the fluid input channel and provides impact fluid through the fluid output channel; a driving unit, which is transmission-connected to the linkage unit and is suitable for driving the linkage unit to drive the displacement unit to reciprocate; wherein the displacement unit has two extreme positions during the reciprocating movement along the first direction and the second direction, and the distance between the two extreme positions is in the range of 2.1mm to 2.6mm; the volume of the fluid pump chamber is 120mm 3 Up to 200mm 3 within the range.

[0009] In second aspect, the present invention provides an oral cleaning device, comprising: a holding shell, a nozzle connected to the end of the holding shell, the fluid pumping unit is arranged in the holding shell, and the nozzle is connected to the fluid output channel of the fluid pumping unit; a fluid storage unit, arranged in the holding shell, the water outlet of the fluid storage unit is connected to the fluid input channel of the fluid pumping unit; a driving mechanism, arranged in the holding shell, and the driving mechanism is suitable for driving the eccentric wheel of the fluid pumping unit to rotate.

[0010] In the third aspect, the present invention also provides an oral cleaning device, comprising: a gripping shell, a fluid storage unit, a fluid pumping unit and a driving mechanism. The end of the gripping shell is connected to a nozzle and a brush head; the fluid storage unit is arranged in the gripping shell; the fluid pumping unit is arranged in the gripping shell, comprising: a shell, a fluid pump chamber is formed in the shell, and a fluid input channel and a fluid output channel connected to the fluid pump chamber, the nozzle is connected to the fluid output channel, and the water outlet of the fluid storage unit is connected to the fluid input channel; a displacement unit is movably arranged in the shell, the end face of the displacement unit facing the first direction is enclosed and sealed with the inner wall of the shell to form the fluid pump chamber with a variable volume; a linkage unit is arranged in the shell and is transmission-connected to the end face of the displacement unit facing the second direction, and the linkage unit is suitable for driving the displacement unit along the first direction and the second direction The brush head is reciprocated in the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber, so that the liquid in the fluid storage unit is pumped into the fluid pump chamber through the fluid input channel and the impact fluid is provided through the fluid output channel; the driving unit includes a first driving member and a second driving member arranged in the gripping shell, the first driving member is suitable for driving the brush head to perform a cleaning action, and the second driving member is connected to the linkage unit in a transmission manner and is suitable for driving the linkage unit to drive the displacement unit to reciprocate; wherein, the displacement unit has two extreme positions during the reciprocating movement along the first direction and the second direction, and the distance between the two extreme positions is in the range of 2.1mm to 2.6mm; the volume of the fluid pump chamber is 120mm 3 Up to 165mm 3 within the range. Beneficial effects:

[0011] Utilizing the technical solution of the present invention, the principle of the fluid pumping unit is to increase and decrease the volume of the fluid pump chamber by driving the reciprocating movement of the displacement unit through the linkage unit, so as to increase and decrease the pressure in the fluid pump chamber cyclically. When the volume of the fluid pump chamber is reduced, the water in the fluid storage unit enters the fluid pump chamber under the action of negative pressure. When the volume of the fluid pump chamber is increased, the water in the fluid pump chamber enters the fluid output channel to form an impact water flow, thereby forming a pulse jet. The pulse jet is a non-continuous water flow and can use the water hammer effect to form huge transient energy. Therefore, while reducing water consumption, it can also increase the impact force of the water flow to ensure the cleaning effect. In addition, the distance between the two extreme positions of the displacement unit is in the range of 2.1mm to 2.6mm, and the volume of the fluid pump chamber is 120mm. 3 Up to 165mm 3The impact force of the water flow can be guaranteed within a certain range, and the size of the fluid pumping unit can be reasonably reduced based on this. In this way, the cleaning effect can be guaranteed with less water flow, and the size of the fluid pumping unit and the fluid storage unit can be reduced to a great extent.

[0012] In addition, the nozzle and brush head on the grip shell can realize the functions of an oral irrigator and an electric toothbrush. Users can choose to use the two cleaning methods separately or simultaneously to clean their teeth. The principle of the fluid pumping unit is to drive the reciprocating movement of the displacement unit through the linkage unit to cyclically increase and decrease the volume of the fluid pump chamber, so as to cyclically increase and decrease the pressure in the fluid pump chamber. When the pressure of the fluid pump chamber is reduced, the liquid in the fluid storage unit enters the fluid pump chamber under the action of negative pressure. When the pressure of the fluid pump chamber is increased, the liquid in the fluid pump chamber enters the fluid output channel to form an impact fluid, thereby forming a pulse jet. The pulse jet is a discontinuous fluid and can use the water hammer effect to form huge transient energy. Therefore, while reducing the liquid consumption, it can also increase the impact force of the fluid to ensure the cleaning effect. In addition, the distance between the two extreme positions of the displacement unit is in the range of 2.1mm to 2.6mm, and the volume of the fluid pump chamber is 120mm. 3 Up to 165mm 3 Within the range of the impact force of the water flow, the size of the fluid pumping unit can be reasonably reduced based on this, thereby reducing the size of the holding shell. In the above manner, the oral cleaning appliance can have the cleaning functions of both an electric toothbrush and an irrigator, and while ensuring the fluid impact force, the size of the fluid pumping unit can be reduced, while saving liquid. The volume of the fluid storage unit can also be further reduced, thereby reducing the size of the holding shell and reducing the weight of the oral irrigator, giving users a better experience. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the specific embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0014] FIG1A shows a schematic structural diagram of an oral care appliance according to an embodiment of the present invention;

[0015] FIG1B shows a schematic structural diagram of another oral care appliance according to an embodiment of the present invention;

[0016] FIG2 shows a schematic structural diagram of a fluid pumping unit according to an embodiment of the present invention;

[0017] FIG3 shows a schematic cross-sectional structural diagram of the fluid pumping unit in FIG2 ;

[0018] FIG4 shows an enlarged schematic diagram of point A in FIG3 ;

[0019] FIG5 is a schematic diagram showing the structure of the eccentric wheel and the balancing weight in FIG3;

[0020] FIG6 is a schematic diagram showing the structure of the eccentric wheel and the balancing weight in FIG5 when viewed from above;

[0021] FIG7 is a schematic diagram showing the structure of the eccentric wheel and the balancing weight in FIG5 in a top view;

[0022] FIG8 shows experimental parameters of a fluid pumping unit according to an embodiment of the present invention;

[0023] FIG9 is a schematic diagram showing the relationship between the impact force and the distance between the two extreme positions of the connecting rod;

[0024] FIG10 is a schematic diagram showing the relationship between the pumping time and the distance between the two extreme positions of the connecting rod;

[0025] FIG11 is a schematic diagram showing the relationship between the impact force and the inner diameter of the fluid input channel;

[0026] FIG12 is a schematic diagram showing the relationship between the flow rate per unit time of the fluid pump cavity and the inner diameter of the fluid input channel;

[0027] FIG13 shows a schematic structural diagram of a flushing handle according to an embodiment of the present invention;

[0028] FIG14 is a schematic structural diagram showing the installation positions of the power take-off shaft and the fluid pumping unit according to an embodiment of the present invention;

[0029] FIG15 shows a schematic structural diagram of a connecting member according to an embodiment of the present invention;

[0030] FIG16 is a schematic diagram of the exploded structure of the flushing handle according to an embodiment of the present invention;

[0031] FIG17 shows a schematic diagram of the exploded structure of the power output member and the front and rear shock absorber pads.

[0032] Description of reference numerals:

[0033] 10. Housing; 11. Fluid pump chamber; 12. Fluid input channel; 13. Fluid output channel; 20. Linkage unit; 201. Shaft hole; 21. Rotating shaft; 22. Bearing; 23. Balance block; 30. Connecting rod; 40. Displacement unit; 50. Fluid storage unit; 51. Liquid filling port; 60. Second drive member; 70. Holding shell; 71. Flush handle; 711. Fluid channel; 72. Power output shaft; 721. Axial channel; 722. Outlet; 723. Inlet; 73. First drive member; 74. Connecting member; 741. Connecting chamber; 742. First end; 743. Second end; 744. Annular groove; 75. Mounting groove; 751. Boss; 761. Front shock pad; 762. Rear shock pad; 80. Spray nozzle; 90. Brush head; 901. Contact element carrier; 902. Contact element cluster; 903. Channel. DETAILED DESCRIPTION

[0034] Currently, oral cleaners combine the functions of an oral irrigator and an electric toothbrush, allowing them to clean both teeth and the spaces between teeth simultaneously. Oral cleaning devices consist of a brush head and a nozzle. The brush head scrapes away bacteria and food debris from the tooth surface, while the nozzle flushes away bacteria and food debris from the spaces between teeth. This combination effectively removes bacteria and food debris from both the tooth surface and the spaces between teeth, thereby preventing oral problems and improving oral health.

[0035] To facilitate the flushing function, conventional oral cleaning devices typically use two independent motors to drive the brush head and nozzle, which increases the weight of the device to a certain extent. This is particularly true for the flushing function, which also includes a pump body and a water tank connected to the pump body. During use, the pump body pumps water from the water tank, pressurizing the water flow through the pump body and internal reducing pipes. The water is then ejected from the nozzle, where the pressurized water cleans the user's teeth. To ensure cleaning power, conventional pump bodies are generally large and consume a lot of water. To meet the water requirements of the pump body, the volume of the water tank must be increased, further increasing the weight of the oral cleaning device. This also increases the size of the oral cleaning device, making it difficult for the user to hold and reducing the user experience. Conventional improvements involve reducing the volume of the water tank while keeping the pump body unchanged. While this reduces the size of the handle to a certain extent, it affects the water output of the nozzle, which reduces cleaning power and affects the cleaning effect. Therefore, conventional oral cleaning devices fail to resolve the contradiction between product size and cleaning power.

[0036] Based on this, the present application provides a fluid pumping unit and an oral cleaning device to solve the problem of the contradiction between product size and cleaning power in the existing water flosser.

[0037] To make the purpose, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making creative efforts shall fall within the scope of protection of the present invention.

[0038] As shown in FIG. 1A and FIG. 2 to FIG. 4 , a fluid pumping unit of an oral cleaning appliance according to the present application includes: a housing 10 , a displacement unit 40 , a linkage unit 20 and a driving unit, wherein the driving unit is a second driving member 60 .

[0039] A fluid pump chamber 11 is formed within the housing 10, along with a fluid input channel 12 and a fluid output channel 13 communicating with the fluid pump chamber 11. Since the fluid pump chamber 11 primarily utilizes changes in internal pressure to achieve liquid inflow and outflow, one-way valves can be provided on the fluid input channel 12 and the fluid output channel 13, respectively. The one-way valve in the fluid input channel 12 allows liquid to flow from the fluid storage unit to the fluid pump chamber 11, while the one-way valve in the fluid output channel 13 allows liquid to flow from the fluid pump chamber 11 to the fluid output channel 13. The liquid can be water, mouthwash, or oral care solution, for example. The fluid storage unit 50 is used to hold the liquid. For ease of description, water will be used as an example.

[0040] Furthermore, the fluid input channel 12 is connected to the fluid storage unit 50, and the fluid output channel 13 is connected to the nozzle 80. When the pressure in the fluid pump chamber 11 increases, the water in the fluid pump chamber 11 flows out of the nozzle 80 through the fluid output channel 13, and the one-way valve of the fluid input channel 12 prevents the water in the fluid pump chamber 11 from entering the fluid input channel 12; when the pressure in the fluid pump chamber 11 decreases, the water in the fluid storage unit 50 enters the fluid pump chamber 11 through the fluid input channel 12, and the one-way valve of the fluid output channel 13 prevents the water in the fluid output channel 13 from flowing back into the fluid pump chamber 11.

[0041] The displacement unit 40 is movably arranged in the shell 10, and the end face of the displacement unit 40 facing the first direction is enclosed and sealed with the inner wall of the shell 10 to form a fluid pump chamber 11 with variable volume. In this embodiment, the edge of the displacement unit 40 can be fitted with the inner wall of the shell 10, so that the inner wall located in the first direction of the shell 10 can be enclosed and sealed with the diaphragm to form a chamber, which is the fluid pump chamber 11. The displacement unit 40 is movably arranged so that the volume of the fluid pump chamber 11 can be variable. The fluid input channel 12 and the fluid output channel 13 are also located in the first direction and are connected to the fluid pump chamber 11. Due to the setting of the one-way valve, when the volume of the fluid pump chamber 11 changes, the pressure in the fluid pump chamber 11 will also increase or decrease, so that negative pressure can be used to suck liquid from the fluid input channel 12 into the fluid pump chamber 11, or pressure can be used to pump liquid from the fluid pump chamber 11 into the fluid output channel 13.

[0042] As shown by the dotted arrow in Figure 3, with the displacement unit 40 as the boundary, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, and the linkage unit 20 that drives the displacement unit 40 to move is located in a second direction opposite to the first direction. Such a setting is conducive to dry and wet separation, and the liquid will not enter the movement space of the linkage unit 20, avoiding affecting the linkage unit 20 and other electrical components.

[0043] The linkage unit 20 is arranged in the housing 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction. The linkage unit 20 is suitable for driving the displacement unit 40 to reciprocate along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 is pumped into the fluid pump chamber 11 through the fluid input channel 12, and the impact fluid is provided through the fluid output channel 13.

[0044] As shown in the first direction and the second direction in Figure 3, the displacement unit 40 reciprocates along the first direction and the second direction. The displacement unit 40 extends into the fluid pump chamber 11, and the displacement unit 40 cyclically increases and decreases the volume of the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 is pumped into the fluid pump chamber 11 through the fluid input channel 12, and provides impact fluid through the fluid output channel 13. The second driving member 60 is transmission-connected to the linkage unit 20, and is suitable for driving the linkage unit 20 to drive the displacement unit 40 to reciprocate. Among them, the displacement unit 40 has two extreme positions during the reciprocating movement along the first direction and the second direction, and the distance between the two extreme positions is in the range of 2.1mm to 2.6mm. The volume of the fluid pump chamber 11 is 120mm 3 Up to 165mm 3 within the range.

[0045] Specifically, a sealed space is formed by the displacement unit 40, the sidewalls of the fluid pump chamber 11, the one-way valve of the fluid input channel 12, and the one-way valve of the fluid output channel 13. The movement of the displacement unit 40 can change the volume of the sealed space, and the pressure within the fluid pump chamber 11 will increase or decrease accordingly. When the pressure within the fluid pump chamber 11 decreases, liquid is pumped from the fluid storage unit 50 through the fluid input channel 12 into the fluid pump chamber 11 under the action of negative pressure. When the pressure within the fluid pump chamber 11 increases, the liquid is discharged from the fluid pump chamber 11 through the fluid output channel 13, forming an impact water flow. Since the fluid pump chamber 11 needs to suck in the liquid and then discharge it, a discontinuous pulse jet is formed in the fluid output channel 13. The water hammer pressure of the pulse jet is greater than the stagnation pressure of the continuous jet. In principle, the pulse water flow can use the water hammer effect to generate huge transient energy, thereby increasing the impact force of the impact water flow, thereby improving the cleaning effect. Compared with continuous water flow, the pulse water flow can save water, which can reduce the volume of the fluid storage unit and reduce the size of the fuselage.

[0046] Based on this, the distance between the two extreme positions of the displacement unit 40 is set within the range of 2.1mm to 2.6mm. This range is sufficient to meet the requirements of the pressure change in the fluid pump chamber 11. Then, the space in the housing 10 used to support the movement of the linkage unit 20 can be reduced accordingly, thereby reducing the design size of the housing 10 and the size of the fuselage. Using the technical solution of this embodiment, the linkage unit 20 drives the displacement unit 40 to move back and forth, so that the fluid output channel 13 forms a pulse jet. While ensuring the impact force, it can also save liquid consumption. The use of a smaller volume fluid storage unit can meet the liquid consumption requirements. At the same time, the distance between the two extreme positions of the displacement unit 40 is 2.1mm to 2.6mm. This setting reduces the space in the housing 10 that supports the movement of the linkage unit 20 and the displacement unit 20, and reduces the size of the housing 10.

[0047] In one implementation of this embodiment, the linkage unit 20 includes an eccentric wheel and a connecting rod 30 .

[0048] The eccentric is located in the housing 10 in a second direction opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 offset from its geometric center. The rotation axis 21 passes through the eccentric and extends along the eccentric's rotation axis. The rotation axis is parallel to and does not overlap with the eccentric's central axis. A connecting rod 30 is located between the displacement unit 40 and the eccentric. The first end of the connecting rod 30 is rotatably connected to the eccentric so that when the eccentric rotates, the connecting rod 30 is driven to reciprocate in a direction perpendicular to the rotation axis 21. The second end of the connecting rod 30 extends toward the displacement unit 40 and is connected to the end surface of the displacement unit 40 facing the second direction. During the reciprocating movement of the connecting rod 30, the displacement unit 40 is driven to increase and decrease the volume within the fluid pump chamber 11 in the same stroke cycle as the connecting rod 30, thereby pumping water within the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 and providing impact fluid through the fluid output channel 13. The second end of the connecting rod 30 has two extreme positions during the reciprocating motion, one close to the rotation axis 21 and the other far away from the rotation axis 21 , and the distance between the two extreme positions is in the range of 2.1 mm to 2.6 mm.

[0049] As shown by the dotted arrow in Figure 3, with the displacement unit 40 as the boundary, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, and the connecting rod 30 and the eccentric wheel that drive the displacement unit 40 to move are located in a second direction opposite to the first direction. Such an arrangement is conducive to dry and wet separation, and the liquid will not enter the movement space of the connecting rod 30 and the eccentric wheel, thereby avoiding affecting the linkage unit 20 and other electrical components.

[0050] The connecting rod 30 is arranged in the housing 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction. The connecting rod 30 is suitable for driving the displacement unit 40 to reciprocate along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 is pumped into the fluid pump chamber 11 through the fluid input channel 12, and the impact fluid is provided through the fluid output channel 13.

[0051] The eccentric is located in a second direction within the housing 10, opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 offset from its geometric center. The eccentric is adapted to rotate about the rotation axis 21. The rotation axis 21 extends through the eccentric and along the eccentric's rotational axis. The rotational axis is parallel to and does not coincide with the eccentric's central axis. The geometric center of the eccentric is the center of the eccentric's geometric shape. Therefore, when the eccentric rotates about the rotation axis 21, it performs an eccentric rotational motion.

[0052] The connecting rod 30 is located between the displacement unit 40 and the eccentric. The first end of the connecting rod 30 is rotatably connected to the eccentric so that when the eccentric rotates, the connecting rod 30 is driven to reciprocate in a direction perpendicular to the rotation axis 21. The second end of the connecting rod 30 extends in a direction away from the rotation axis 21, as shown in the first and second directions in FIG3 , and the displacement unit 40 reciprocates in the first and second directions. The first end of the connecting rod 30 can serve as a power input end, and the first end of the connecting rod 30 can rotate around the rotation center under the drive of the eccentric. The second end opposite the first end can serve as a power output end, and the second end of the connecting rod 30 can reciprocate perpendicular to the rotation axis 21.

[0053] The displacement unit 40 is connected to the second end of the connecting rod 30 and extends into the fluid pump chamber 11. The displacement unit 40 acts on a plane in the fluid pump chamber 11 that is parallel to the rotation axis 21. During the reciprocating movement of the connecting rod 30, the displacement unit 40 cyclically increases and decreases the volume of the fluid pump chamber 11, so that the water in the fluid storage unit 50 in the oral cleaning device is pumped into the fluid pump chamber 11 through the fluid input channel 12 and provides an impact water flow through the fluid output channel 13. In particular, during the reciprocating movement, the second end of the connecting rod 30 has two extreme positions, one close to the rotation axis 21 and the other away from the rotation axis 21, with the distance between the two extreme positions being in the range of 2.1mm to 2.6mm. The volume of the fluid pump chamber 11 is 120mm. 3 Up to 165mm 3 within the range.

[0054] Based on this, the distance between the two extreme positions of the connecting rod 30 is set within a range of 2.1 mm to 2.6 mm. This range is sufficient for the displacement unit 40 to meet the pressure fluctuation requirements within the fluid pump chamber 11. This can correspondingly reduce the space within the housing 10 required to support the movement of the connecting rod 30, thereby reducing the design dimensions of the housing 10 and the size of the device. Utilizing the technical solution of this embodiment, the rotation of the eccentric wheel drives the displacement unit 40 back and forth through the second end of the connecting rod 30, causing the fluid output channel 13 to form a pulsed jet. While ensuring impact force, it also saves liquid consumption, allowing a smaller fluid storage unit to meet liquid consumption requirements. Furthermore, the distance between the two extreme positions of the connecting rod 30 is 2.1 mm to 2.6 mm. This configuration reduces the space within the housing 10 required to support the movement of the connecting rod 30, thereby reducing the size of the housing 10. The second drive member 60 is a brushless motor disposed within the grip housing 70. The rotating shaft 21 is the output shaft of the brushless motor. The speed of the brushless motor is within the range of 3500 mrp to 4500 mrp. The brushless motor has excellent torque characteristics and a wide speed regulation range, so there is no need to set up an additional gear box, which further simplifies the structure and reduces the size of the grip housing 70.

[0055] The fluid storage unit is shown in Figure 3. The dotted arrows in the figure indicate the effective movement direction of the connecting rod 30, which requires the connecting rod 30 to reciprocate in the first and second directions. The two extreme positions of the connecting rod 30 are located in the first and second directions, respectively. When the connecting rod 30 moves to the extreme position in the first direction, the diaphragm discharges the liquid in the fluid pump chamber 11. When the connecting rod 30 moves to the extreme position in the second direction, the diaphragm is at the maximum distance from the opposite side of the fluid pump chamber 11, reducing the pressure in the fluid pump chamber 11 and allowing liquid to enter the fluid pump chamber 11 from the fluid input channel 12.

[0056] As shown in Figures 3 and 4, the edge of the displacement unit 40 is fixedly set on the side wall of the fluid pump chamber 11, the displacement unit 40 and the second end of the connecting rod 30 can be connected by screws, and the displacement unit 40 can be integrally injection molded with the screws, which simplifies the structure and reduces the difficulty of assembly.

[0057] As shown in Figures 3 and 4, the housing 10 has a cavity for accommodating the eccentric wheel, and the second driving member 60 is located at the bottom of the housing 10. The output shaft of the second driving member 60 extends into the cavity and is coupled to the eccentric wheel to form a rotating shaft 21. The driving unit can drive the eccentric wheel to rotate through the rotating shaft 21. For example, a shaft knurling can be provided on the rotating shaft 21, and the eccentric wheel is pressed onto the shaft knurling. The shaft knurling can increase the friction between the rotating shaft 21 and the eccentric wheel to ensure that the rotating shaft 21 can smoothly drive the eccentric wheel to rotate. A shaft seat is provided in the cavity, and the end of the output shaft of the second driving member 60 can extend into the shaft seat to improve the stability of the output shaft rotation. In addition to providing space for the above components, the cavity also needs to provide a certain amount of movement space for the rotation of the eccentric wheel and the reciprocating motion of the first end of the connecting rod 30. The distance between the two extreme positions of the connecting rod 30 is set to 2.1mm to 2.6mm to limit the size of the movement space in the cavity, and based on this, the overall design size of the housing 10 can be reduced.

[0058] The applicant has demonstrated through a large amount of experimental data that if the distance between the two extreme positions of the connecting rod 30 is less than 2.1 mm, the pumping force will be weakened, and the water flow rate of the pump will be insufficient, which cannot meet the requirements of the water flow impact force; if the distance between the two extreme positions of the connecting rod 30 is greater than 2.6 mm, the design size of the cavity is too large and cannot meet the requirements of reducing the overall design size of the shell 10. Therefore, the distance between the two extreme positions of the connecting rod 30 is set at 2.1 mm to 2.6 mm, for example, it can be 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm or 2.6 mm.

[0059] In this embodiment, the first end of the connecting rod 30 coincides with the geometric center of the eccentric relative to the rotational center of the eccentric, and the eccentricity of the eccentric is within a range of 1.05 mm to 1.3 mm. When the rotational center of the first end of the connecting rod 30 coincides with the collective center of the eccentric, the travel of the second end of the connecting rod is twice the eccentricity of the eccentric. Setting the eccentricity of the eccentric within a range of 1.05 mm to 1.3 mm ensures that the distance between the two extreme positions of the connecting rod 30 is within a range of 2.1 mm to 2.6 mm.

[0060] As shown in Figures 4 and 5, in this embodiment, the cross-section of the eccentric is configured to be circular, perpendicular to the rotation axis 21. The first end of the connecting rod 30 is provided with a sleeve, the axis of which is parallel to the rotation axis 21 and is disposed outside the eccentric. The eccentric has an axial hole 201 that mates with the rotation axis 21. The eccentric is configured as a circle, and the sleeve can also be configured as a circle, thereby reducing friction between the eccentric and the first end of the connecting rod 30, ensuring that the first end of the connecting rod 30 can perform reciprocating circular motion through the sleeve and the outer edge of the eccentric. With the eccentric rotating 360° around the rotation axis 21 as one complete stroke of the connecting rod 30, the first end of the connecting rod 30 performs reciprocating circular motion, which is more conducive to controlling the distance between the two extreme positions of the connecting rod 30 to be between 2.1 mm and 2.6 mm, thereby ensuring that the movement of the displacement unit 40 can provide a stable pressure differential.

[0061] In order to further reduce the friction between the eccentric wheel and the sleeve hole, a bearing 22 can be set between the eccentric wheel and the connecting rod 30. The bearing 22 is sleeved on the eccentric wheel, and the sleeve hole is sleeved on the bearing 22. The bearing 22 can reduce the friction between the eccentric wheel and the connecting rod 30, and prevent the eccentric wheel from driving the connecting rod to rotate coaxially, so as to ensure that the connecting rod 30 can perform a cyclic reciprocating motion in a direction perpendicular to the rotating shaft 21.

[0062] Since the center of mass of the eccentric is not located on the axis of the rotating shaft 21, an unbalanced centrifugal force will be generated during the rotation of the eccentric. The generated unbalanced torque increases the burden on the output shaft of the second drive member 60, increasing the friction resistance of the axle and the heat generation.

[0063] To solve the above problems, as shown in Figures 5, 6 and 7, in this embodiment, a balancing weight 23 is connected to the eccentric wheel. The balancing weight 23 is suitable for increasing the weight at the rotating shaft 21 of the eccentric wheel to balance the torque of the eccentric wheel during rotation. Specifically, the weights of the balancing weight 23 are different at opposite ends. The heavier end is arranged at the top of the shaft hole 201, which extends to the end surface of the balancing weight 23 and passes through the balancing weight 23. The lighter end is arranged at the top of the side opposite to the shaft hole 201. This arrangement can increase the mass of one side of the rotating shaft 21, thereby making the weights of the eccentric wheel on opposite sides of the rotating shaft 21 equal or nearly equal. Then, when the eccentric wheel rotates, the centrifugal force at both ends of the eccentric wheel is equal, solving the problem of unbalanced centrifugal force at both ends of the eccentric wheel, thereby balancing the torque of the output shaft of the second drive member 60, making the rotation of the output shaft of the second drive member 60 more stable, reducing the friction resistance of the axle protrusion, and reducing heat generation. In addition, arranging the balancing weight 23 on the top of the eccentric wheel can avoid motion interference between the balancing weight 23 and the connecting rod 30, thereby avoiding interference with the transmission of the eccentric wheel and the connecting rod 30.

[0064] In one specific implementation of this embodiment, the cross-section of the balancing weight 23 can be symmetrical. The dashed lines in Figures 6 and 7 indicate the axis of symmetry of the balancing weight 23. This configuration avoids introducing new unbalanced forces. Specifically, using the orientation shown in Figure 7 as an example, the balancing weight 23 has two arcuate sides in the left and right directions, with the left arcuate side being shorter than the right arcuate side, and a hypotenuse in the vertical direction, which slopes outward toward the right arc. This makes the right side dimension of the balancing weight 23 larger than the right side dimension. If the density of the balancing weight 23 is uniform, that is, the right side weight of 23 is greater than the left side weight, thereby balancing the centrifugal forces on the left and right sides when the eccentric wheel rotates.

[0065] Of course, the structure of the balancing weight 23 can also be adaptively adjusted by simply increasing the weight at the shaft hole 201 of the eccentric wheel.

[0066] In this embodiment, the eccentric wheel and the balancing weight 23 are integrally formed, which is convenient for production and reduces assembly errors. Fasteners can also be used, such as screws to fix the balancing weight 23 to the eccentric wheel, making it convenient to adjust or replace the balancing weight 23 later.

[0067] In another implementation of this embodiment, the second driving member 60 is a linear motor arranged in the gripping shell 70, and the linkage unit 20 is the output shaft of the linear motor. The stroke of the output shaft is in the range of 2.1 mm to 2.6 mm. The output shaft of the linear motor drives the displacement unit 40 to perform reciprocating motion to provide cyclically increasing and decreasing pressure to the fluid pump chamber 11.

[0068] In this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3Up to 165mm 3 The water output per unit time of the fluid output channel 13 is related to the volume of the fluid pump chamber 11. Specifically, the water output per unit time of the fluid output channel 13 increases with the increase of the volume of the fluid pump chamber 11. When the diameter of the fluid output channel 13 remains unchanged, the impact force of the water flow increases with the increase of the water output per unit time. After a large number of experimental demonstrations, the applicant found that when the distance between the two extreme positions of the connecting rod 30 is 2.2mm to 2.4mm, the volume of the fluid pump chamber 11 is 120mm. 3 Up to 165mm 3 If the volume of the fluid pump chamber 11 is less than 120mm, the pressure of the fluid output channel 13 can meet both the impact force requirement and the water saving requirement. 3 , the water flow is too small to meet the impact force requirements; if the volume of the fluid pump chamber 11 is greater than 165mm 3 Although the impact force requirement can be met, the excessive amount of water discharged per unit time means that the consumption of water in the fluid storage unit 50 will be accelerated, resulting in failure to meet the cleaning time requirement and affecting the cleaning effect.

[0069] Further preferably, in this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm 3 In the case that the distance between the two extreme positions of the connecting rod 30 during the reciprocating movement is within the range of , the distance between the two extreme positions of the connecting rod 30 during the reciprocating movement is selected to be 2.2 mm.

[0070] For example, the volume of the fluid pump chamber 11 may be 120 mm 3 , 121mm 3 , 122mm 3 , 123mm 3 ...or 130mm 3 As shown in Figure 3, when the second end of the connecting rod 30 moves to the extreme position in the first direction, the diaphragm can completely fit against the side wall of the fluid pump chamber 11, thereby completely draining the liquid in the fluid pump chamber 11. If the extreme position is greater than 2.2 mm, the diaphragm will interfere with the side wall of the fluid pump chamber 11 during the movement of the second end of the connecting rod 30 to the extreme position in the first direction.

[0071] Further preferably, in this embodiment, the volume of the fluid pump chamber is 155mm 3 Up to 165mm 3 In the case that the range is within the range, the distance between the two extreme positions of the connecting rod during the reciprocating movement is selected to be 2.4mm.

[0072] For example, the volume of the fluid pump chamber 11 may be 155 mm 3 , 156mm3 , 157mm 3 , 158mm 3 ...or 165mm 3 As shown in FIG3 , when the second end of the connecting rod 30 moves to the extreme position in the first direction, the diaphragm can completely fit against the side wall of the fluid pump chamber 11, thereby completely draining the liquid in the fluid pump chamber 11. If the extreme position is less than 2.4 mm, a gap will exist between the diaphragm and the side wall of the fluid pump chamber 11 when the second end of the connecting rod 30 moves to the extreme position in the first direction, thereby reducing the operating efficiency of the fluid pump chamber 11.

[0073] In this embodiment, by optimizing various parameters of the fluid pumping unit, the fluid pumping unit is made more water-saving while ensuring the cleaning power, so that the size of the fluid storage unit in the oral cleaning device can be made smaller, thereby solving the contradiction between the product size and cleaning power of the water flosser in the prior art.

[0074] The above is an explanation of the principle of movement of the various components of the fluid pumping unit in this embodiment. The following is a detailed introduction to the basis for determining the values ​​of various parameters in the fluid pumping unit in this embodiment.

[0075] 1. The distance between the two extreme positions of the connecting rod 30 during reciprocating motion

[0076] To change the size of the oral cleaning appliance, it is necessary to give priority to the large-volume components in the oral cleaning appliance. Currently, the volume of the fluid pumping unit and the volume of the fluid storage unit have a direct impact on the size of the oral cleaning appliance. The fluid pumping unit not only needs to provide a storage space for each moving part, but also needs to provide a movement space for each moving part. Therefore, the connecting rod 30 can be improved from the perspective of the storage space and the movement space. In order to select the optimal distance range between the two extreme positions in the reciprocating motion of the connecting rod 30, while controlling other parameters unchanged and only changing the distance between the two extreme positions in the reciprocating motion of the connecting rod 30, the applicant obtained the following four groups of experimental data through experiments, refer to Figure 8:

[0077] Sample 1: The distance is 2.0 mm, the impact force is 0.041 N to 0.062 N, and the time required to pump out 200 ml of water is 75 seconds to 89 seconds.

[0078] Sample 2: The distance is 2.2mm, the impact force is 0.90N to 0.98N, and the time required to pump out 200ml of water is 54 seconds to 68 seconds.

[0079] Sample 3: The distance is 2.4mm, the impact force is 0.107N to 0.114N, and the time required to pump out 200ml of water is 47 seconds to 49 seconds.

[0080] Sample 4: The distance is 2.6mm, the impact force is 0.127N to 0.130N, and the time required to pump out 200ml of water is 40 seconds to 43 seconds.

[0081] A greater impact force indicates stronger cleaning power, while a smaller impact force indicates weaker cleaning power. A shorter time to pump out 200ml of water means more water is used, while a longer time means more water is saved. From the above experimental data, it can be seen that when cleaning power is greater, water consumption increases, so it is necessary to balance these two conditions.

[0082] Furthermore, as the distance between the two extreme positions of the connecting rod 30 increases during its reciprocating motion, the diaphragm's ability to deform concavely and convexly increases, thereby increasing the inflow and outflow rates of the fluid pump chamber 11. The greater the outflow rate, the greater the impact force in the fluid output channel 13. The applicant has experimentally determined that an impact force ≥ 0.07 N satisfies oral hygiene requirements. Therefore, a standard impact force ≥ 0.07 N can be used as a basis for subsequent experiments to determine other design parameters.

[0083] In sample 1, although it takes a long time to draw out 200ml of water, which can achieve the purpose of saving water, its cleaning power does not meet the requirements and cannot meet the needs of oral cleaning, so it was discarded.

[0084] In sample 4, although the impact force is large, the time required to pump out 200ml of water is too short, and it is likely that it cannot meet the cleaning time once, so it is eliminated.

[0085] In samples 2 and 3, the impact force was sufficient and the time required to pump out 200 ml of water was relatively reasonable, so they were retained.

[0086] In summary, in this embodiment, the two extreme positions of the connecting rod 30 during the reciprocating motion are ultimately determined to be between 2.2 mm and 2.4 mm. Within this range, the water output per unit time can be satisfied, the standard impact force requirements can be met, and the water output per unit time can be controlled within a certain range, without increasing the volume of the fluid storage unit 50. Specifically, if the distance between the two extreme positions of the connecting rod 30 is less than 2.2 mm, the water flow rate will be insufficient and the water impact force requirements cannot be met. If the distance between the two extreme positions of the connecting rod 30 is greater than 2.4 mm, the design size of the cavity is too large, which cannot meet the requirement of reducing the overall design size of the housing 10. At the same time, the water output per unit time will increase, and a larger volume of the fluid storage unit 50 will be required to provide sufficient water storage capacity.

[0087] 2. Volume Range of Fluid Pump Chamber 11

[0088] The volume of the fluid pump chamber 11 in this embodiment is related to the flow rate of water discharged by the diaphragm after a complete concave-convex deformation. Therefore, the volume of the fluid pump chamber 11 must not only meet the requirements of sufficient flow rate per unit time, but also meet the requirements of the deformation stroke of the diaphragm. The flow rate per unit time of the fluid pump chamber 11 is related to the speed of the motor. In this embodiment, the speed n of the motor is preferably set to 3500mrp to 4500mrp. If the speed n of the motor is less than 3500mrp, it cannot be guaranteed that the calculated flow rate per unit time of the fluid pump chamber 11 meets the requirements. If the speed n of the motor is greater than 4500mrp, it will cause excessive noise. The flow rate per unit time of the fluid pump chamber 11 can be calculated by the following formula: Q 流体泵腔 =nv. Among them, Q 流体泵腔 is the flow rate per unit time of the fluid pump chamber 11. n is the speed of the motor, that is, the speed of the eccentric wheel. v is the volume of the fluid pump chamber 11. From the above formula, the calculated flow rate per unit time of the fluid pump chamber 11 can be calculated. When the diameter of the fluid output channel 13 remains unchanged, the formula: F = 10.2ρQ 流体泵腔 2 The jet impact force is calculated by ΔF / A, where F is the jet impact force and ρ is the density of the jet medium, which can be water. A is the cross-sectional area of ​​the jet pipeline, which includes at least the cross-sectional area of ​​the fluid output channel 13 and the nozzle used for oral cleaning.

[0089] Refer to the experimental data shown in Figure 8:

[0090] Sample 1, distance is 2.0mm, volume of fluid pump chamber 11 is 120mm 3 Up to 130mm 3 Although it takes a long time to pump 200ml of water, the impact force is only 0.041N to 0.062N, which does not meet the standard impact force requirements and is therefore rejected. Comparing Sample 1 and Sample 2, it can be found that although the volume of the fluid pump chamber 11 has not changed, the smaller distance in Sample 1 cannot ensure that the diaphragm maintains high working efficiency.

[0091] Sample 4, distance is 2.6mm, volume of fluid pump chamber 11 is 155mm 3 Up to 165mm 3 Although it can meet the standard requirements of impact force, compared with sample 3, sample 3 can save more water while meeting the impact force requirements, so sample 4 is eliminated.

[0092] Figure 9 is a schematic diagram showing the relationship between the impact force and the distance between the two extreme positions of the connecting rod. The dotted line corresponds to the minimum impact force, and the solid line corresponds to the maximum impact force. The analysis is as follows:

[0093] It should be noted that, considering that the utilization rate of the fluid pump chamber 11 is restricted by the limit position of the connecting rod 30 and the volume of the fluid pump chamber 11, it is necessary to ensure that the utilization rate of the fluid pump chamber 11 is maintained at a high level as much as possible. Among them, the main influencing factor is the following standard: during the process of the connecting rod 30 completing a stroke, whether the diaphragm can be completely attached to the side wall when it moves to the limit distance in the direction of the fluid pump chamber 11. Based on this, the following four sets of data are obtained to ensure that the utilization rate of the fluid pump chamber 11 is at a high level. For example, the distance between the two limit positions of the connecting rod 30 is 2.0 mm, and the volume of the fluid pump chamber is 120 mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.2mm, and the volume of the fluid pump chamber is 120mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.4mm, and the volume of the fluid pump chamber is 155mm 3 Up to 165mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.6mm, and the volume of the fluid pump chamber is 155mm 3 Up to 165mm 3 .

[0094] As can be seen from the dotted lines in Figure 9, as the distance between the two extreme positions of the connecting rod 30 increases, the minimum impact force does not increase proportionally. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the minimum impact force shows a first increasing trend. When it is in the range of 2.2mm to 2.4, the change in the minimum impact force shows a first decreasing trend. When it is in the range of 2.4mm to 2.6, the change in the minimum impact force shows a second increasing trend. Due to the differences in the volume of the fluid pump chamber 11 in the above data, it can be divided into the following three situations:

[0095] The first case is that the volume of the fluid pump chamber 11 is 120mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod is in the range of 2.0mm to 2.2mm. As the distance between the two extreme positions of the connecting rod 30 increases, the impact force also increases. This is because the increase in the distance between the two extreme positions of the connecting rod 30 directly affects the utilization rate of the fluid pump chamber 11, that is, the stroke of the diaphragm is increased, thereby increasing the water inlet capacity of the fluid pump chamber 11, which also directly affects the flow rate of the fluid pump chamber 11 per unit time, thereby increasing the impact force.

[0096] The second case is that the volume of the fluid pump chamber 11 is 155mm 3 Up to 165mm 3Within the range, the distance between the two extreme positions of the connecting rod 30 is in the range of 2.4mm to 2.6mm. As the distance between the two extreme positions of the connecting rod 30 increases, the impact force also increases. This is because the increase in the distance between the two extreme positions of the connecting rod 30 directly affects the utilization rate of the fluid pump chamber 11, that is, it increases the stroke of the diaphragm, thereby increasing the water inlet capacity of the fluid pump chamber 11, which also directly affects the flow rate of the fluid pump chamber 11 per unit time, thereby increasing the impact force.

[0097] In the third case, the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 Up to 165mm 3 Within the range, the distance between the two extreme positions of the connecting rod 30 is 2.4 mm. From the changing trend, although the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 increase, the minimum impact force decreases. Therefore, it is confirmed that the impact force does not tend to increase proportionally with the increase of the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30.

[0098] From the comparison between Case 1 and Case 2, when the volume of the fluid pump chamber 11 is the same, as the distance between the two extreme positions of the connecting rod 30 increases, the utilization rate of the fluid pump chamber 11 gradually increases, the water output increases, and the impact force also gradually increases, and the first growth trend is smaller than the second growth trend. This means that when the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 are large, the impact force increases more with the increase in the distance between the two extreme positions of the connecting rod 30, making it easier to meet the requirement of a larger impact force. This means that when the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 are small, it is easier to meet the requirement of a stable impact force. From Case 3, in addition to the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11, there are other factors that affect the impact force.

[0099] As can be seen from the solid line in Figure 9, as the distance between the two extreme positions of the connecting rod 30 increases, the maximum impact force does not increase proportionally. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the maximum impact force shows the third growth trend. In the range of 2.2mm to 2.4, the change in the maximum impact force shows the fourth growth trend. In the range of 2.4mm to 2.6, the change in the maximum impact force shows the fifth growth trend. There is a clear difference between the third growth trend, the fourth growth trend, and the fifth growth trend. Figure 10 is a schematic diagram of the relationship between the pumping time and the distance between the two extreme positions of the connecting rod, where the dotted line corresponds to the shortest time and the solid line corresponds to the longest time. The analysis is as follows:

[0100] As can be seen from the dotted lines in Figure 10, as the distance between the two extreme positions of the connecting rod 30 increases, the shortest time does not show a proportional decreasing trend. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the shortest time shows a first downward trend. When it is in the range of 2.2mm to 2.4mm, the change in the shortest time shows a first upward trend. When it is in the range of 2.4mm to 2.6mm, the change in the shortest time shows a second downward trend. The shorter the pumping time, the greater the actual flow rate of the fluid pump chamber 11 per unit time, and the more water is consumed. It can be divided into the following three situations:

[0101] The first case is that the volume of the fluid pump chamber 11 is 120mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod is in the range of 2.0mm to 2.2mm. As the distance between the two extreme positions of the connecting rod 30 increases, the shortest time becomes shorter, which corresponds to the analysis results of Figure 9 above. The impact force also increases. It is not difficult to judge that as the distance between the two extreme positions of the connecting rod 30 increases, the flow rate per unit time in the fluid pump chamber 11 will also increase, thereby increasing the impact force, which confirms the above analysis.

[0102] The second case is that the volume of the fluid pump chamber 11 is 155mm 3 Up to 165mm 3 Within the range of , the distance between the two extreme positions of the connecting rod 30 is in the range of 2.4mm to 2.6mm. As the distance between the two extreme positions of the connecting rod 30 increases, the shortest time becomes shorter. Corresponding to the analysis of Figure 9 above, the impact force also increases. It is not difficult to judge that as the distance between the two extreme positions of the connecting rod 30 increases, the flow rate per unit time of the fluid pump chamber 11 will also increase, thereby increasing the impact force, which confirms the above analysis.

[0103] In the third case, the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm3 The distance between the two extreme positions of the connecting rod 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 Up to 165mm 3 Within the range, the distance between the two extreme positions of the connecting rod 30 is 2.4 mm. From the changing trend, although the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 increase, the shortest time becomes longer, corresponding to the analysis of Figure 9 above, the minimum impact force decreases, which confirms the above analysis.

[0104] Judging from the solid line in Figure 10, as the distance between the two extreme positions of the connecting rod 30 becomes farther, the maximum time does not show a trend of decreasing in equal proportion. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the maximum time shows the third downward trend. When it is in the range of 2.2mm to 2.4, the change in the maximum time shows the fourth downward trend. When it is in the range of 2.4mm to 2.6, the change in the maximum time shows the fifth downward trend. There are obvious differences between the third downward trend, the fourth downward trend and the fifth downward trend.

[0105] Through the above two analysis processes, it can be seen that the water output per unit time of the fluid pump chamber 11 has become a factor affecting the impact force. And from the overall perspective, when the volume of the fluid pump chamber 11 is in a small range, it is necessary to ensure that the distance between the two extreme positions of the connecting rod 30 meets the requirements to ensure that the fluid pump chamber 11 has sufficient efficiency. Moreover, the volume of the fluid pump chamber 11 cannot be too small to ensure sufficient water output to meet the impact force requirements. When the volume of the fluid pump chamber 11 is in a large range, it is necessary to reasonably control the distance between the two extreme positions of the connecting rod 30 to control the actual flow rate of the fluid pump chamber 11 per unit time to meet the water saving requirements.

[0106] Therefore, if the volume of the fluid pump chamber 11 is less than 120 mm 3 , it will lead to insufficient water output, and without changing the water outlet cross-sectional area, it will not be able to meet the standard requirements of the impact force; if the volume of the fluid pump chamber 11 is greater than 165mm 3 , will result in excessive water output per unit time, although it can meet the standard requirements of impact force, it will accelerate the consumption of water in the fluid storage unit 50. Increasing the volume of the fluid storage unit 50 can meet the water demand, but it will undoubtedly increase the overall size of the oral cleaning appliance. Therefore, the volume of the fluid pump chamber 11 is 120mm 3 Up to 165mm 3 The standard requirements for impact force can be met within the range, and the flow rate of the fluid pump chamber 11 per unit time can be controlled, thereby achieving the purpose of saving water and reducing the volume of the fluid storage unit 50.

[0107] Since the distance between the two extreme deformation strokes of the diaphragm corresponds to the distance between the two extreme positions of the connecting rod 30 during movement, under the premise of ensuring the maximum efficiency of the fluid pump chamber 11, it can be specifically divided into at least the following two situations:

[0108] The first case is that when the distance between the two extreme positions of the connecting rod 30 during the reciprocating motion is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 Up to 130mm 3 As shown in FIG3 , when the second end of the connecting rod 30 moves to the extreme position in the first direction, the diaphragm can be completely attached to the side wall of the fluid pump chamber 11, thereby completely discharging the liquid in the fluid pump chamber 11 to achieve the maximum efficiency of the fluid pump chamber 11. If the volume of the fluid pump chamber 11 is greater than 130mm 3 When the second end of the connecting rod 30 moves to the extreme position in the first direction, a gap will exist between the diaphragm and the side wall of the fluid pump chamber 11, thereby reducing the efficiency of the fluid pump chamber 11.

[0109] The second case is that when the distance between the two extreme positions of the connecting rod 30 during the reciprocating motion is 2.4 mm, the volume of the fluid pump chamber 11 is 155 mm. 3 Up to 165mm 3 As shown in FIG3 , when the second end of the connecting rod 30 moves to the extreme position in the first direction, the diaphragm can be completely attached to the side wall of the fluid pump chamber 11, thereby completely discharging the liquid in the fluid pump chamber 11 to achieve the maximum efficiency of the fluid pump chamber 11. If the volume of the fluid pump chamber 11 is less than 155mm 3 , it may cause the side wall of the fluid pump chamber 11 to interfere with the diaphragm, resulting in the diaphragm being unable to complete the deformation stroke of the limit distance of 2.4 mm.

[0110] In this embodiment, the ratio of the calculated flow rate per unit time of the fluid pump chamber to the actual flow rate per unit time of the fluid output channel can satisfy the following relationship: K = Q 流体泵腔 / Q 流体输出通道 Where K is the ratio of the calculated flow rate per unit time of the fluid pumping unit to the actual flow rate per unit time of the fluid output channel. When K is within the range of 2.93≦K≦3.75, Q 流体泵腔 Calculate the flow rate per unit time of the fluid pump cavity, Q 流体输出通道 is the actual flow rate per unit time of the fluid output channel, that is, the actual flow rate per unit time can be determined by measuring the actual water outflow rate of the fluid output channel 13.

[0111] Through extensive experimental data, the applicant has discovered that the smaller the K value, the more liquid flows out of fluid output channel 13 per unit time, resulting in a greater impact force. A larger K value, however, results in less liquid flowing out of fluid output channel 13 per unit time, resulting in a smaller impact force. Based on the standard requirements for impact force, when the K value is greater than 3.75, the impact force of fluid output channel 13 fails to meet the standard requirements. When the K value is less than 2.93, while the standard requirements are met, the actual flow rate per unit time increases, resulting in excessive liquid consumption and failing to meet water conservation requirements.

[0112] Furthermore, Q 流体泵腔 and Q 流体输出通道 The difference is caused by the pressure loss caused by the resistance along the way encountered by water in the liquid pipeline. For example, in addition to the fluid input channel 12 and the fluid output channel 13 introduced in this embodiment, the water will also pass through elbows, tees, reducers, valves and other components after leaving the fluid storage unit 50 or before entering the nozzle 80. The flow state of the water will change dramatically, that is, turning, acceleration, collision, vortex, deformation and the like will occur, which will cause pressure loss, and it will make it impossible to pump the water into the fluid pump chamber 11 according to the calculated data, and it will also be impossible to completely discharge the water in the fluid pump chamber 11 according to the calculated displacement.

[0113] 3. Inner Diameter Range of Fluid Input Channel 12

[0114] The principle of replenishing the fluid pump chamber 11 is to use negative pressure to pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12. The inner diameter of the fluid input channel 12 affects the liquid's resistance along the flow path. Through extensive experimental data, the applicant has found that the smaller the inner diameter of the fluid input channel 12, the greater the liquid's resistance along the flow path, the less liquid enters the fluid pump chamber 11, the smaller the actual flow rate of the fluid output channel 13, and the smaller the impact force of the water flow. The larger the inner diameter of the fluid input channel 12, the smaller the liquid's resistance along the flow path, the more liquid enters the fluid pump chamber 11, the greater the actual flow rate of the fluid output channel 13, and the greater the impact force of the water flow.

[0115] Refer to the experimental data shown in Figure 8:

[0116] Sample 2: The distance is 2.2 mm, and the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm 3. When the inner diameter of the fluid input channel 12 is 2.0mm, the actual flow rate per unit time is 174ml / min, and the impact force is 0.067N; when the inner diameter of the fluid input channel 12 is 2.5mm, the actual flow rate per unit time is 182ml / min, and the impact force is 0.067N; when the inner diameter of the fluid input channel 12 is 3.0mm, the actual flow rate per unit time is 235ml / min, and the impact force is 0.094N. From the above data, it can be seen that as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time will also increase, and the impact force is also increasing. Although the impact force is 0.067N when the inner diameter of the fluid input channel 12 is 2.0mm and 2.5mm, which is 0.003N different from the standard impact force, the impact of 0.003N on the cleaning effect can be ignored in actual use.

[0117] Sample 3: The distance is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 Up to 165mm 3 When the inner diameter of the fluid input channel 12 is 2.0 mm, the actual flow rate per unit time is 154 ml / min, and the impact force is 0.06 N. When the inner diameter of the fluid input channel 12 is 2.5 mm, the actual flow rate per unit time is 185 ml / min, and the impact force is 0.072 N. When the inner diameter of the fluid input channel 12 is 3.0 mm, the actual flow rate per unit time is 286 ml / min, and the impact force is 0.104 N. From the above data, it can be seen that as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time also increases, and the impact force also increases.

[0118] FIG11 is a schematic diagram showing the relationship between the impact force and the inner diameter of the fluid input channel. The solid line corresponds to the experimental data of sample 2, and the dotted line corresponds to the experimental data of sample 3. The analysis is as follows:

[0119] As can be seen from the solid line corresponding to Sample 2, when the inner diameter of the fluid input channel 12 increases, the impact force also increases, and the impact force does not increase proportionally according to the coefficient. For example, when the inner diameter of the fluid input channel 12 is between 2.0 mm and 2.5 mm, the impact force hardly changes. However, in the range of 2.5 mm to 3.0 mm, the impact force increases sharply. This is because there are many factors that restrict the actual flow rate of the fluid input channel 12, such as the inner diameter of the fluid input channel 12, the distance between the two extreme positions of the connecting rod 30, the volume of the fluid pump chamber 11, the speed of the motor, etc. This embodiment takes the change of the inner diameter of the fluid input channel 12 as an example. When the inner diameter of the fluid input channel 12 changes, the longitudinal resistance of the fluid input channel 12 also decreases. Therefore, this sudden increase trend only occurs after the longitudinal resistance of the fluid input channel 12 decreases to a certain threshold. Obviously, due to the other factors of Sample 2, it is impossible to effectively overcome the limitation of the longitudinal resistance of the fluid input channel 12 below 2.5 mm on the impact force. Therefore, the distance between the two extreme positions of the connecting rod 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 120 mm. 3 Up to 130mm 3 , the inner diameter of the fluid input channel 12 can be preferably set to be greater than 2.5 mm.

[0120] It can be seen from the dotted line corresponding to sample three that when the inner diameter of the fluid input channel 12 increases, the impact force can also increase, and the change trend of the impact force does not increase proportionally according to the coefficient. For example, the inner diameter of the fluid input channel 12 shows a first trend in the range of 2.0mm to 2.5mm, and the fluid input channel 12 shows a second trend in the range of 2.5mm to 3.0mm. It is not difficult to find that the growth rate of the second trend is greater than the growth rate of the first trend. Therefore, it can be found that when the inner diameter of the fluid input channel 12 is less than 2.5mm, the growth rate of the impact force is small, and when the inner diameter of the fluid input channel 12 is greater than 2.5mm, the growth rate of the impact force is large. In addition, the distance between the two extreme positions of the connecting rod 30 of sample three is 2.4mm, and the volume of the fluid pump chamber 11 is 155mm. 3 Up to 165mm 3 , which can overcome the resistance along the fluid input channel 12 below 2.5 mm, so under the parameters of the connecting rod 30 and the fluid pump chamber 11 of sample three, there is no need to consider the resistance along the fluid input channel 12.

[0121] From the comparison of the solid line corresponding to sample 2 and the dotted line corresponding to sample 3 in Figure 11, it can be seen that, under the same inner diameter of the fluid input channel 12, from the perspective of the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11, although the two data of sample 3 are both greater than the two data of sample 2, when the inner diameter of the fluid input channel 12 is in the range of 2.0mm to 2.5mm, the impact force corresponding to sample 3 is smaller than the impact force corresponding to sample 2. Therefore, it is not the case that under the same inner diameter of the fluid input channel 12, the impact force of sample 3 is always greater than the impact force of sample 2. That is, under the same inner diameter of the fluid input channel 12, the increase in the values ​​of the above two data does not increase in proportion to the coefficient. Therefore, it is necessary to reasonably select the inner diameter of the fluid input channel 12 corresponding to samples 2 and 3 to meet the impact force requirements.

[0122] For example, as can be seen from FIG11 , only when the inner diameter of the fluid input channel 12 is greater than 2.5 mm can the impact force of sample 2 gradually meet the basic requirements of the impact force. Therefore, without considering other variables, the inner diameter of the fluid input channel 12 corresponding to sample 2 is preferably greater than 2.5 mm.

[0123] FIG12 is a schematic diagram showing the relationship between the flow rate per unit time of the fluid pump cavity and the inner diameter of the fluid input channel, wherein the solid line corresponds to the experimental data of sample 2, and the dotted line corresponds to the experimental data of sample 3. The analysis is as follows:

[0124] As can be seen from the solid line corresponding to Sample 2, when the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pump chamber 11 can also increase. Moreover, the change trend of the flow rate per unit time of the fluid pump chamber 11 does not increase proportionally according to the coefficient. For example, when the inner diameter of the fluid input channel 12 is between 2.0mm and 2.5mm, the flow rate per unit time of the fluid pump chamber 11 hardly changes. However, in the range of 2.5mm to 3.0mm, the flow rate per unit time of the fluid pump chamber 11 shows a trend of sudden increase. Therefore, it is not difficult to see that although the resistance along the fluid input channel 12 decreases when the inner diameter of the fluid input channel 12 changes, this sudden increase trend only occurs after the resistance along the fluid input channel 12 decreases to a certain threshold. This also confirms the conclusion of the analysis of Figure 11. Obviously, due to the constraints of other factors in Sample 2, it is impossible to effectively overcome the limitation of the impact force on the resistance along the fluid input channel 12 below the inner diameter of 2.5mm. Therefore, when the distance between the two extreme positions of the connecting rod 30 is 2.2mm, the volume of the fluid pump chamber 11 is 120mm. 3 Up to 130mm 3 , the inner diameter of the fluid input channel 12 can be preferably set to be greater than 2.5 mm.

[0125] From the dotted line corresponding to sample three, it can be seen that when the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pump chamber 11 can also increase, and the change trend of the flow rate per unit time of the fluid pump chamber 11 does not increase proportionally according to the coefficient. For example, the inner diameter of the fluid input channel 12 shows a first trend in the range of 2.0mm to 2.5mm, and the fluid input channel 12 shows a second trend in the range of 2.5mm to 3.0mm. It is not difficult to find that the growth rate of the second trend is greater than the growth rate of the first trend. Therefore, it can be found that when the inner diameter of the fluid input channel 12 is less than 2.5mm, the growth rate of the flow rate per unit time of the fluid pump chamber 11 is small, and when the inner diameter of the fluid input channel 12 is greater than 2.5mm, the growth rate of the flow rate per unit time of the fluid pump chamber 11 is large. It can be seen that there is a corresponding relationship between the flow rate per unit time of the fluid pump chamber 11 and the impact force. Moreover, the distance between the two extreme positions of the connecting rod 30 of sample three is 2.4mm, and the volume of the fluid pump chamber 11 is 155mm. 3 Up to 165mm 3 , the flow rate per unit time of the fluid pump chamber 11 of sample three can still show an increasing trend, which confirms the analysis conclusion of Figure 11. The parameters of the fluid pump chamber 11 and the connecting rod 30 of sample three can overcome the along-the-path resistance of the fluid input channel 12 below 2.5 mm. Therefore, under the parameters of the connecting rod 30 and the fluid pump chamber 11 of sample three, there is no need to consider the along-the-path resistance of the fluid input channel 12.

[0126] From the comparison of the solid line corresponding to sample 2 and the dotted line corresponding to sample 3 in Figure 12, it can be seen that under the same inner diameter of the fluid input channel 12, from the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11, although the two data of sample 3 are greater than the two data of sample 2, when the inner diameter of the fluid input channel 12 is in the range of 2.0mm to 2.5mm, the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 3 is less than the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 2, which confirms the analysis conclusion in Figure 11. Therefore, it is necessary to reasonably select the inner diameters of the fluid input channels 12 corresponding to samples 2 and 3 to meet the requirements of the flow rate and impact force per unit time of the fluid pump chamber 11.

[0127] Therefore, the inner diameter of the fluid input channel 12 needs to be reasonably selected according to the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11 to meet the standard requirements of the impact force.

[0128] Optionally, the inner diameter of the fluid input channel 12 is within the range of 2.0 mm to 3.0 mm. For example, the inner diameter of the fluid input channel 12 can be 2.0 mm, 2.1 mm, 2.2 mm, ... or 3.0 mm. The inner diameters of the above fluid input channels 12 can all meet the impact force requirements, while the actual flow rate per unit time of the fluid output channel 13 can be controlled, thereby achieving the purpose of saving water. If the inner diameter of the fluid input channel 12 is less than 2.0 mm, the actual flow rate per unit time of the fluid output channel 13 will be too small, and will not be able to meet the standard requirements for the impact force; if the inner diameter of the fluid input channel 12 is greater than 3.0 mm, although the standard requirements for the impact force can be met, the actual flow rate per unit time of the fluid output channel 13 will be too large, and the purpose of saving water will not be achieved.

[0129] Preferably, the inner diameter of the fluid input channel is in the range of 2.5 mm to 3.0 mm. For example, the inner diameter of the fluid input channel 12 can be 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, or 3.0 mm. The inner diameters of the fluid input channel 12 can meet the optimal cleaning requirements while saving water, thereby improving the cleaning effect.

[0130] In one implementation of this embodiment, the displacement unit 40 is a diaphragm. The edge of the diaphragm is attached to the side wall of the housing 10 in the second direction, so the end surface of the diaphragm facing the first direction and the side wall of the housing 10 in the first direction enclose and seal to form a sealed space with variable volume, which is the fluid pump chamber 11. The end surface of the diaphragm facing the second direction is connected to the linkage unit 20, so that the diaphragm can be deformed concavely and convexly under the drive of the linkage unit 20 to change the volume of the fluid pump chamber 11, and then change the pressure of the fluid pump chamber 11. Referring to Figure 3, taking the linkage unit 20 as an example of the connection between the connecting rod 30 and the eccentric wheel:

[0131] The eccentric is located in a second direction within the housing 10, opposite to the first direction of the diaphragm. The eccentric has a rotation axis 21 offset from its geometric center. The eccentric is adapted to rotate about this axis 21. The axis 21 extends through the eccentric and along its rotational axis, which is parallel to and non-coincident with the eccentric's central axis. The geometric center of the eccentric is the center of its geometric shape. Therefore, when the eccentric rotates about the axis 21, it performs an eccentric rotational motion.

[0132] The connecting rod 30 is located between the diaphragm and the eccentric. The first end of the connecting rod 30 is rotatably connected to the eccentric so that when the eccentric rotates, the connecting rod 30 is driven to reciprocate in a direction perpendicular to the rotation axis 21. The second end of the connecting rod 30 extends in a direction away from the rotation axis 21, as shown in the first and second directions in Figure 3, and the diaphragm reciprocates in the first and second directions. The first end of the connecting rod 30 can serve as a power input end, and the first end of the connecting rod 30 can rotate about the rotation center under the drive of the eccentric. The second end opposite the first end can serve as a power output end, and the second end of the connecting rod 30 can reciprocate perpendicular to the rotation axis 21.

[0133] The diaphragm is connected to the second end of the connecting rod 30 and extends into the fluid pump chamber 11. The plane in the fluid pump chamber 11 on which the diaphragm acts is arranged parallel to the rotating shaft 21. During the reciprocating movement of the connecting rod 30, the diaphragm cyclically increases and decreases the volume in the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 in the oral cleaning appliance is pumped into the fluid pump chamber 11 through the fluid input channel 12, and the impact fluid is provided through the fluid output channel 13.

[0134] Specifically, a sealed space is formed by the diaphragm, the sidewalls of the fluid pump chamber 11, the one-way valve in the fluid input channel 12, and the one-way valve in the fluid output channel 13. The diaphragm's concave-convex deformation changes the volume of the sealed space, which in turn increases or decreases the pressure within the fluid pump chamber 11. When the pressure within the fluid pump chamber 11 decreases, liquid is pumped from the fluid storage unit 50 through the fluid input channel 12 into the fluid pump chamber 11 under the influence of negative pressure. When the pressure within the fluid pump chamber 11 increases, liquid is discharged from the fluid pump chamber 11 through the fluid output channel 13, forming a percussive fluid. Since the fluid pump chamber 11 needs to suck in the liquid and then discharge it, a discontinuous pulse jet is formed in the fluid output channel 13. The water hammer pressure of the pulse jet is greater than the stagnation pressure of the continuous jet. In principle, the pulse water flow can use the water hammer effect to generate huge transient energy, thereby increasing the impact force of the impact water flow, thereby improving the cleaning effect. Compared with continuous water flow, the pulse water flow can save liquid, which can reduce the volume of the fluid storage unit and reduce the size of the fuselage.

[0135] Based on this, the distance between the two extreme positions of the connecting rod 30 is set within the range of 2.1mm to 2.6mm. This range is sufficient to allow the diaphragm to effectively deform concavely and convexly to meet the pressure change requirements in the fluid pump chamber 11. Then, the space in the housing 10 used to support the movement of the connecting rod 30 can be reduced accordingly, thereby reducing the design size of the housing 10 and the size of the fuselage. Using the technical solution of this embodiment, the rotation of the eccentric wheel drives the diaphragm to reciprocate through the second end of the connecting rod 30, so that the fluid output channel 13 forms a pulse jet. While ensuring the impact force, it can also save the amount of liquid used, and a smaller volume of fluid storage unit can be used to meet the liquid volume requirements. At the same time, the distance between the two extreme positions of the connecting rod 30 is 2.1mm to 2.6mm. This setting reduces the space in the housing 10 that supports the movement of the connecting rod 30 and reduces the size of the housing 10.

[0136] In another embodiment of the present invention, the displacement unit 40 is a piston. Unlike the previous embodiment, the movement of the diaphragm is concave-convex deformation. Therefore, the inner wall of the housing 10 located in the first direction of the diaphragm needs to be set to a corresponding concave surface, while the movement of the piston is to slide along the inner wall of the housing 10 through the edge. That is, when the end face of the piston facing the first direction is a plane, the inner wall of the housing 10 can be set to a plane. When the end face of the piston facing the first direction is an arc surface, the inner wall of the housing 10 can be set to a corresponding concave surface. Compared with the diaphragm, the piston has a stronger compression capacity and is less likely to form gaps. The end face of the piston facing the second direction is connected to the linkage unit 20. The movement principle of the piston is the same as that of the diaphragm, and will not be repeated here.

[0137] As shown in FIG. 1A and FIG. 2 , in this embodiment, an oral cleaning appliance is provided, comprising: a gripping shell 70 , the fluid pumping unit mentioned above, a fluid storage unit 50 , and a driving mechanism.

[0138] A nozzle 80 is connected to the end of the grip housing 70. The fluid pumping unit is disposed within the grip housing 70, and the nozzle 80 is in communication with the fluid output channel 13 of the fluid pumping unit. The fluid storage unit 50 is disposed within the grip housing 70, and the outlet of the fluid storage unit 50 is in communication with the fluid input channel 12 of the fluid pumping unit. A drive mechanism is disposed within the grip housing 70 and is adapted to drive the eccentric wheel of the fluid pumping unit to rotate.

[0139] The oral cleaning device in this embodiment is a water irrigator. The water irrigator uses the impact force of water flow to clean teeth. Based on the aforementioned reduced design size and water consumption of the fluid pumping unit, the size of the fluid storage unit 50 can also be reduced accordingly, thereby reducing the design size of the grip housing 70 and improving the user experience.

[0140] In this embodiment, the diameter of the liquid outlet of the nozzle is in the range of 0.6 mm to 0.65 mm. For example, the diameter of the liquid outlet of the nozzle can be 0.6 mm, 0.61 mm, 0.62 mm, 0.63 mm, 0.64 mm or 0.65 mm.

[0141] In this embodiment, the driving mechanism includes a second driving member 60, and the rotation speed of the second driving member 60 is in the range of 3500 rpm to 4500 rpm. Within this range, the flow rate of the fluid pump chamber 11 per unit time can be guaranteed. According to the formula Q 流体泵腔 =nv,Q 流体泵腔 Within the range of 542ml / min to 693ml / min, the K value can be within the range of 2.93 to 3.75. It should be noted that due to the existence of resistance along the way, the calculated flow rate per unit time of the fluid pump chamber 11 and the flow rate per unit time of the nozzle 80 are in a certain proportional relationship. The larger the K value, the smaller the flow rate per unit time of the nozzle, and the more water can be saved.

[0142] In this embodiment, the volume of the fluid storage unit 50 is in the range of 50 ml to 200 ml. Within this range, the amount of water stored in the fluid storage unit 50 is sufficient to meet the requirements for teeth cleaning.

[0143] In this embodiment, the capacity of the fluid storage unit 50 is 50 ml. The capacity of the fluid storage unit 50 is related to the volume. Reducing the volume of the fluid storage unit 50 is beneficial to reducing the size of the grip housing 70.

[0144] In this embodiment, the fluid storage unit 50 is disposed below the fluid pumping unit and at the bottom of the grip housing 70. A liquid inlet 51 is provided on the underside of the grip housing 70, communicating with the fluid storage unit 50. In other words, the fluid storage unit 50 and the fluid pumping unit are arranged along the extension of the grip housing 70. This reduces the size of the grip housing 70 in the gripping direction, making it easier for the user to grip the grip housing 70. The liquid inlet 51 is used to refill the fluid storage unit 50. A removable end cap is provided on the liquid inlet 51, which can be opened to complete the refilling operation.

[0145] As shown in FIG. 1A , in this embodiment, the oral cleaning appliance is an integrated rinsing oral cleaning appliance, and a brush head 90 is further provided at the end of the gripping shell 70 .

[0146] The integrated oral cleaning device can be an integrated irrigator, which combines the functions of an irrigator and an electric toothbrush, and can simultaneously clean both teeth and the spaces between teeth. It can effectively remove bacteria and food debris from the tooth surfaces and between teeth, thereby preventing oral problems and improving oral health. For example, the friction of the brush head 90 can be used to remove impurities from the tooth surface, while the impact force of the nozzle 80 can be used to impact debris in the spaces between teeth, thereby achieving a good cleaning effect.

[0147] In the integrated oral cleaner of this embodiment, the fluid storage unit 50 is arranged at the bottom of the gripping shell 70, and the brush head 90 is located at the top of the gripping shell 70. Therefore, the gravity at the top of the gripping shell 70 is relatively small. As the amount of water in the fluid storage unit 50 decreases, the center of gravity of the gripping shell can always be located in the middle position of the gripping shell 70, giving the user a good gripping experience.

[0148] On the basis that the above-mentioned fluid pumping unit can reduce the design size and water consumption, the size of the fluid storage unit 50 can also be reduced accordingly, and the weight of the integrated oral cleaner can also be reduced. The user generally brushes his teeth for about two minutes, and will not feel sore arms or fingers due to long-term holding, thereby improving the user experience.

[0149] As shown in FIG. 1B and FIG. 2 to FIG. 4 , an oral cleaning appliance is provided according to the present application, including: a gripping shell 70 , a brush head 90 , a fluid storage unit 50 , a fluid pumping unit and a driving unit.

[0150] The gripping shell 70 is the gripping part when the user uses the oral cleaning device for cleaning. It accommodates most of the components that realize the cleaning function, such as the above-mentioned fluid storage unit, fluid pumping unit, driving unit, and other pipelines.

[0151] The end of the gripping housing 70 is connected to a nozzle 80 and a brush head 90. The nozzle 80 and the brush head 90 are located on the same side of the end of the gripping housing 70. The brush head 90 has multiple contact element clusters, each of which is formed by a cluster of multiple contact elements. The contact elements can be brush filaments, and the nozzle 80 is located between the multiple contact element clusters. The nozzle 80 is connected to the fluid pumping unit to achieve the function of flushing the teeth. The brush head 90 is connected to the first driving member 73 in the gripping housing to achieve the function of brushing teeth. Therefore, the oral cleaning device provided in this embodiment can achieve the function of both an electric toothbrush and an oral irrigator, thereby improving the cleaning effect of the oral cavity. The fluid storage unit 50 is arranged in the gripping housing 70. The water pump cavity has a fluid input channel 12 connected to the fluid storage unit 50 and a fluid output channel 13 connected to the nozzle 80. The fluid pumping unit can pump the liquid in the fluid storage unit 50 into the nozzle 80 and spray it out, thereby cleaning the teeth or the gaps between the teeth. The liquid may be water, mouthwash, oral care liquid, etc., and the fluid storage unit 50 is used to contain the liquid.

[0152] A fluid pump chamber 11 is formed within the housing 10, and a fluid input channel 12 and a fluid output channel 13 are connected to the fluid pump chamber 11. Since the fluid pump chamber 11 primarily utilizes changes in internal pressure to achieve liquid inflow and outflow, one-way valves can be provided on the fluid input channel 12 and the fluid output channel 13, respectively. The one-way valve on the fluid input channel 12 allows liquid to flow from the fluid storage unit to the fluid pump chamber 11, while the one-way valve on the fluid output channel 13 allows liquid to flow from the fluid pump chamber 11 to the fluid output channel 13.

[0153] Furthermore, when the pressure in the fluid pump chamber 11 increases, the liquid in the fluid pump chamber 11 flows out of the nozzle 80 through the fluid output channel 13, and the one-way valve of the fluid input channel 12 prevents the liquid in the fluid pump chamber 11 from entering the fluid input channel 12; when the pressure in the fluid pump chamber 11 decreases, the liquid in the fluid storage unit 50 enters the fluid pump chamber 11 through the fluid input channel 12, and the one-way valve of the fluid output channel 13 prevents the liquid in the fluid output channel 13 from flowing back into the fluid pump chamber 11.

[0154] The displacement unit 40 is movably arranged in the shell 10, and the end face of the displacement unit 40 facing the first direction is enclosed and sealed with the inner wall of the shell 10 to form a fluid pump chamber 11 with variable volume. In this embodiment, the edge of the displacement unit 40 can be fitted with the inner wall of the shell 10, so that the inner wall located in the first direction of the shell 10 can be enclosed and sealed with the diaphragm to form a chamber, which is the fluid pump chamber 11. The displacement unit 40 is movably arranged so that the volume of the fluid pump chamber 11 can be variable. The fluid input channel 12 and the fluid output channel 13 are also located in the first direction and are connected to the fluid pump chamber 11. Due to the setting of the one-way valve, when the volume of the fluid pump chamber 11 changes, the pressure in the fluid pump chamber 11 will also increase or decrease, so that negative pressure can be used to suck liquid from the fluid input channel 12 into the fluid pump chamber 11, or pressure can be used to pump liquid from the fluid pump chamber 11 into the fluid output channel 13.

[0155] As shown by the dotted arrow in Figure 3, with the displacement unit 40 as the boundary, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, and the linkage unit 20 that drives the displacement unit 40 to move is located in a second direction opposite to the first direction. Such a setting is conducive to dry and wet separation, and the liquid will not enter the movement space of the linkage unit 20, avoiding affecting the linkage unit 20 and other electrical components.

[0156] The linkage unit 20 is arranged in the housing 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction. The linkage unit 20 is suitable for driving the displacement unit 40 to reciprocate along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 is pumped into the fluid pump chamber 11 through the fluid input channel 12, and the impact fluid is provided through the fluid output channel 13.

[0157] As shown in the first and second directions in FIG3 , the displacement unit 40 reciprocates along the first and second directions. The displacement unit 40 extends into the fluid pump chamber 11. The displacement unit 40 cyclically increases and decreases the volume of the fluid pump chamber 11 so that the liquid in the fluid storage unit 50 is pumped into the fluid pump chamber 11 through the fluid input channel 12 and provides impact fluid through the fluid output channel 13. The drive unit includes a first drive member 73 and a second drive member 60 disposed in the grip housing 70. The first drive member 73 is adapted to drive the brush head 90 to swing left and right to clean the teeth. The second drive member 60 is connected to the linkage unit 20 and adapted to drive the linkage unit 20 to drive the displacement unit 40 to reciprocate. For example, the first drive member 73 can be a vibration motor for driving the brush head 90 to vibrate to realize the function of an electric toothbrush. The displacement unit 40 has two extreme positions during the reciprocating movement along the first and second directions. The distance between the two extreme positions is in the range of 2.1 mm to 2.6 mm. The volume of the fluid pump chamber 11 is 120 mm.3 Up to 165mm 3 within the range.

[0158] Specifically, a sealed space is formed by the displacement unit 40, the sidewalls of the fluid pump chamber 11, the one-way valve of the fluid input channel 12, and the one-way valve of the fluid output channel 13. The movement of the displacement unit 40 can change the volume of the sealed space, and the pressure within the fluid pump chamber 11 will increase or decrease accordingly. When the pressure within the fluid pump chamber 11 decreases, liquid is pumped from the fluid storage unit 50 through the fluid input channel 12 into the fluid pump chamber 11 under the action of negative pressure. When the pressure within the fluid pump chamber 11 increases, the liquid is discharged from the fluid pump chamber 11 through the fluid output channel 13, forming an impact water flow. Since the fluid pump chamber 11 needs to suck in the liquid and then discharge it, a discontinuous pulse jet is formed in the fluid output channel 13. The water hammer pressure of the pulse jet is greater than the stagnation pressure of the continuous jet. In principle, the pulse water flow can use the water hammer effect to generate huge transient energy, thereby increasing the impact force of the impact water flow, thereby improving the cleaning effect. Compared with continuous water flow, the pulse water flow can save water, which can reduce the volume of the fluid storage unit and reduce the size of the fuselage.

[0159] Based on this, the distance between the two extreme positions of the displacement unit 40 is set within the range of 2.1mm to 2.6mm. This range is sufficient to meet the requirements of the pressure change in the fluid pump chamber 11. Then, the space in the housing 10 used to support the movement of the linkage unit 20 can be reduced accordingly, thereby reducing the design size of the housing 10 and the size of the fuselage. Using the technical solution of this embodiment, the linkage unit 20 drives the displacement unit 40 to move back and forth, so that the fluid output channel 13 forms a pulse jet. While ensuring the impact force, it can also save liquid consumption. The use of a smaller volume fluid storage unit can meet the liquid consumption requirements. At the same time, the distance between the two extreme positions of the displacement unit 40 is 2.1mm to 2.6mm. This setting reduces the space in the housing 10 that supports the movement of the linkage unit 20 and the displacement unit 20, and reduces the size of the housing 10.

[0160] As shown in Figures 1B, 13, and 14, in this embodiment, a flushing handle 71 is connected to the top of the gripping housing 70. A brush head 90 is mounted at the end of the flushing handle 71. The flushing handle 71 has a fluid channel 711 therein. A nozzle 80 is mounted at the end of the flushing handle 71 and communicates with the fluid output channel 13 via the fluid channel 711. The fluid pump chamber 11 can pump liquid into the fluid channel 711 through the fluid output channel 13, and the liquid can be sprayed out through the nozzle 80. The first drive member 73 includes a power output shaft 72 extending from the gripping housing 70. The flushing handle 71 is connected to the power output shaft 72 and is controlled by the power output shaft 72 to perform a cleaning action. Driven by the first drive member 73, the power output shaft 72 can drive the flushing handle 71 to vibrate, causing the brush head 90 at the top of the flushing handle 71 to swing synchronously to clean the tooth surface. Such a configuration allows the flushing handle 71 to not only drive the brush head 90 to swing, but also supply liquid to the nozzle 80 through the fluid channel 711, so that the oral cleaning device of this embodiment not only has the brushing function of an electric toothbrush, but also has the flushing function of an irrigator, so as to improve the user experience and the cleaning effect of the oral care equipment, and has a synchronous flushing function.

[0161] In this embodiment, the power output shaft 72 can be made of stainless steel, specifically 303 steel or 304 steel, and the vibration motor can drive the power output shaft 72 to reciprocate relative to the holding shell 70.

[0162] As shown in Figure 14, in this embodiment, the first driving member 73 can be a vibration motor. The power output shaft 72 is a cylindrical body that extends through the upper and lower ends of the first driving member 73 and defines an axial channel 721. The axial channel 721 has an outlet connected to the fluid channel 711 and an inlet connected to the fluid output channel 13. The cylindrical body has a hollow interior, forming the axial channel 721, the outlet 722, and the inlet 723 on the power output shaft 72. Liquid pumped from the fluid output channel 13 enters the axial channel 721 through the inlet 723 and continues to flow from the outlet 722 into the fluid channel 711. This allows liquid to be transported directly through the axial channel 721 of the power output shaft 72, eliminating the need for additional liquid pipelines connecting the fluid channel 711 and the fluid output channel 13. This makes the pipeline layout in the grip housing 70 more rational, reduces the number of fluid pipelines, and saves space. This further reduces the size of the grip housing 70, making it easier for users to hold and operate, and improving user comfort.

[0163] In this embodiment, the inner wall of the axial channel 721 of the power output shaft 72 is surface-smoothed, for example, a polishing process can be used to improve the smoothness of the inner wall of the axial channel 721, which is beneficial to reducing the resistance to water flow, thereby ensuring that the impact force of the water flow is reduced due to the resistance along the way, and further ensuring that the liquid sprayed from the nozzle 80 has sufficient impact force to clean the teeth or the gaps between teeth.

[0164] To ensure that the power output shaft 72 has a sufficient service life, the hardness of the power output shaft 72 in this embodiment ranges from Rockwell hardness HRC: 17 to 70, and the single-side wall thickness ranges from 0.3 mm to 1 mm. The applicant has discovered through extensive experimentation that there is an approximate correspondence between the various hardness values ​​of a material and between the hardness value and the strength value. The hardness value is determined by the resistance to plastic deformation. The higher the strength of the material, the higher the resistance to plastic deformation, and the higher the hardness value. Generally, the higher the hardness of a material, the better its wear resistance and the more brittle it is. Therefore, in order to simultaneously ensure the hardness and toughness of the power output shaft 72, it is necessary to reasonably limit the hardness of the power output shaft 72. Setting the hardness of the power output shaft 72 to the above-mentioned range can ensure that the hardness of the power output shaft 72 can meet the power output requirements of the vibration motor, effectively avoiding the problem of plastic deformation of the power output shaft 72 due to insufficient hardness, and also avoiding the problem of excessive brittleness and easy fracture caused by excessive hardness. After the axial channel 721 is opened, the power output shaft 72 can still have good hardness and toughness, and can ensure the power output capacity while meeting the fluid transportation requirements, and ensure the service life and working stability of the first drive member 73.

[0165] Considering that when the power output shaft 72 reciprocates under the drive of the first driving member 73, the axial channel 721 will also reciprocate, and the axial channel 721 will swing relative to the fluid output channel 13. The relative position of the inlet 723 of the axial channel 721 and the fluid output channel 13 will change, resulting in a gap at the connection position between the two, which is not conducive to forming a stable liquid supply relationship between the inlet 723 and the fluid output channel 13.

[0166] In order to solve the above problems, as shown in Figures 14 and 15, in this embodiment, a connecting member 74 is provided between the inlet 723 and the fluid output channel 13. The connecting member 74 has a communicating cavity 741, a first end 742 facing the fluid output channel, and a second end 743 facing the inlet 723. The fluid output channel 13 extends into the first end 742 of the connecting member 74, and the inlet 723 extends into the second end 743 of the connecting member 74.

[0167] The second end 743 and the first end 742 can form stable connections with the inlet 723 and the fluid output channel 13 respectively, and no gap will appear at their respective connection positions.

[0168] In another embodiment, the second end 743 can swing relative to the first end 742. Then, when the power output shaft 72 moves, the liquid can also enter the axial channel 721 through the first end 742, the connecting cavity 741 and the second end 743, so that the second end 743 and the first end 742 form a stable liquid supply relationship, and then a stable liquid supply relationship is formed between the fluid output channel 13 and the axial channel 721, overcoming the problem that the relative position of the axial channel 721 of the power output shaft 72 and the fluid output channel 13 will change.

[0169] The connecting member 74 may be integrally formed on the fluid output channel 13 and connected to the inlet 723 via the second end 743 .

[0170] As shown in FIG. 15 , in this embodiment, the connecting member 74 has an annular groove 744 arranged around the first end 742 . The annular groove 744 provides space for deformation of the connecting member 74 , facilitating the swinging of the second end 743 relative to the first end 742 .

[0171] In this embodiment, the end of the flushing handle 71 has a mounting groove 75, and the mounting groove 75 has a boss 751. The boss 751 is formed in the mounting groove 75 and extends toward the opening of the mounting groove 75. The boss 751 has a liquid outlet of the fluid channel 711. The nozzle 80 is installed on the boss 751. The nozzle 80 has a flow diameter different from the liquid outlet so as to increase the impact force of the jet.

[0172] As shown in FIG16 , in this embodiment, the brush head 90 includes a contact element carrier 901 mounted in the mounting slot 75, and a plurality of contact element clusters 902 spaced apart on the contact element carrier 901. The contact element carrier 901 is provided with a channel 903 corresponding in shape to the nozzle 80. The channel 903 allows the nozzle 80 to extend, allowing the plurality of contact element clusters 902 and the nozzle 80 to be located on the same side of the irrigator handle 71, facilitating the simultaneous use of the functions of a toothbrush and an irrigator to clean teeth.

[0173] In this embodiment, one end of the nozzle 80 connected to the liquid outlet has an annular boss, and the size of the channel 903 is smaller than the size of the annular boss, so that the channel 903 can press the nozzle 80 against the liquid outlet to prevent the water pressure at the liquid outlet from causing the nozzle 80 to fall off.

[0174] Of course, the nozzle 80 and the brush head 90 can also be integrally formed and installed on the installation groove 75 .

[0175] When using the oral cleaning device provided in this embodiment, the user can hold the gripping housing 70, align the nozzle 80 and the brush head 90 with the corresponding positions of the teeth and the gaps between the teeth, and can selectively use the nozzle 80 and the brush head 90 to clean the teeth or the gaps between the teeth. The gripping housing 70 serves as the main carrier for installing the fluid pumping unit, the fluid storage unit 50, and the drive unit. While the impact force of the nozzle 80 can be guaranteed, the size and weight of the gripping housing 70 are greatly reduced by reducing the volume of the fluid storage unit 50 and the size of the housing 10. This greatly reduces the overall size and weight of the oral cleaning device, allowing the user to easily use the oral cleaning device to clean the oral cavity, thereby improving the user experience.

[0176] As shown in Figure 17, in this embodiment, a front shock-absorbing pad 761 is further provided in the holding shell 70, which is mounted on the front end of the first driving member 73, and the front end of the first driving member 73 is installed in the holding shell 70 through the front shock-absorbing pad 761; and a rear shock-absorbing pad 762 is mounted on the rear end of the first driving member 73, and the rear end of the first driving member 73 is installed in the holding shell 70 through the rear shock-absorbing pad 762. The first drive member 73 cooperates with the grip housing 70 via the front and rear shock-absorbing pads 761, 762. The front and rear shock-absorbing pads 761, 762 can be used to prevent the first drive member 73 from directly contacting the grip housing 70. Therefore, the shock-absorbing properties of the front and rear shock-absorbing pads 761, 762 can be used to dampen the first drive member 73, preventing direct contact between the first drive member 73 and the grip housing 70. This can effectively reduce the vibration transmitted from the first drive member 73 to the grip housing 70, thereby reducing the vibration felt by the user when grasping the grip housing 70, reducing vibration noise, and improving the user experience. In this embodiment, the fluid storage unit 50 is disposed on the lower side of the fluid pumping unit and at the bottom of the grip housing 70. A water inlet 51 connected to the fluid storage unit 50 is disposed on the lower side of the grip housing 70. That is, the fluid storage unit 50 and the fluid pumping unit are arranged along the extension direction of the gripping shell 70, so that the size of the gripping shell 70 in the gripping direction can be reduced, so that the user can easily grip the gripping shell 70. The water inlet 51 is used to replenish water to the fluid storage unit 50, and an end cover is movably provided on the water inlet 51. The water replenishment operation can be completed by opening the end cover. In the oral cleaning appliance of this embodiment, the fluid storage unit 50 is arranged at the bottom of the gripping shell 70, and the brush head 90 is located at the top of the gripping shell 70. Therefore, the gravity at the top of the gripping shell 70 is relatively small. As the amount of water in the fluid storage unit 50 decreases, the center of gravity of the gripping shell can always be located in the middle of the gripping shell 70, giving the user a good gripping feeling.

[0177] In addition, the fluid storage unit 50 can also be set on the left or right side of the holding shell 70. The size of the fluid storage unit 50 along the width direction of the holding shell 70 can be reduced by increasing the size of the fluid storage unit 50 along the length direction of the holding shell 70, which can be determined according to actual conditions.

[0178] On the basis that the above-mentioned fluid pumping unit can reduce the design size and water consumption, the size of the fluid storage unit 50 can also be reduced accordingly, and the weight of the oral cleaning appliance can also be reduced. The user generally brushes his teeth for about two minutes, and will not feel sore arms or fingers due to long-term holding, thereby improving the user experience.

[0179] In one implementation of this embodiment, the linkage unit 20 includes an eccentric wheel and a connecting rod 30 .

[0180] The eccentric is located in the housing 10 in a second direction opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 offset from its geometric center. The rotation axis 21 passes through the eccentric and extends along the eccentric's rotation axis. The rotation axis is parallel to and does not overlap with the eccentric's central axis. A connecting rod 30 is located between the displacement unit 40 and the eccentric. The first end of the connecting rod 30 is rotatably connected to the eccentric so that when the eccentric rotates, the connecting rod 30 is driven to reciprocate in a direction perpendicular to the rotation axis 21. The second end of the connecting rod 30 extends toward the displacement unit 40 and is connected to the end surface of the displacement unit 40 facing the second direction. During the reciprocating movement of the connecting rod 30, the displacement unit 40 is driven to increase and decrease the volume within the fluid pump chamber 11 in the same stroke cycle as the connecting rod 30, thereby pumping water within the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 and providing impact fluid through the fluid output channel 13. The second end of the connecting rod 30 has two extreme positions during the reciprocating motion, one close to the rotation axis 21 and the other far away from the rotation axis 21 , and the distance between the two extreme positions is in the range of 2.1 mm to 2.6 mm.

[0181] As shown by the dotted arrow in Figure 3, with the displacement unit 40 as the boundary, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, and the connecting rod 30 and the eccentric wheel that drive the displacement unit 40 to move are located in a second direction opposite to the first direction. Such an arrangement is conducive to dry and wet separation, and the liquid will not enter the movement space of the connecting rod 30 and the eccentric wheel, thereby avoiding affecting the linkage unit 20 and other electrical components.

[0182] The connecting rod 30 is arranged in the housing 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction. The connecting rod 30 is suitable for driving the displacement unit 40 to reciprocate along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 is pumped into the fluid pump chamber 11 through the fluid input channel 12, and the impact fluid is provided through the fluid output channel 13.

[0183] The eccentric is located in a second direction within the housing 10, opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 offset from its geometric center. The eccentric is adapted to rotate about the rotation axis 21. The rotation axis 21 extends through the eccentric and along the eccentric's rotational axis. The rotational axis is parallel to and does not coincide with the eccentric's central axis. The geometric center of the eccentric is the center of the eccentric's geometric shape. Therefore, when the eccentric rotates about the rotation axis 21, it performs an eccentric rotational motion.

[0184] The connecting rod 30 is located between the displacement unit 40 and the eccentric. The first end of the connecting rod 30 is rotatably connected to the eccentric so that when the eccentric rotates, the connecting rod 30 is driven to reciprocate in a direction perpendicular to the rotation axis 21. The second end of the connecting rod 30 extends in a direction away from the rotation axis 21, as shown in the first and second directions in FIG3 , and the displacement unit 40 reciprocates in the first and second directions. The first end of the connecting rod 30 can serve as a power input end, and the first end of the connecting rod 30 can rotate around the rotation center under the drive of the eccentric. The second end opposite the first end can serve as a power output end, and the second end of the connecting rod 30 can reciprocate perpendicular to the rotation axis 21.

[0185] The displacement unit 40 is connected to the second end of the connecting rod 30 and extends into the fluid pump chamber 11. The displacement unit 40 acts on a plane within the fluid pump chamber 11 parallel to the rotation axis 21. During the reciprocating movement of the connecting rod 30, the displacement unit 40 cyclically increases and decreases the volume of the fluid pump chamber 11, thereby pumping water from the fluid storage unit 50 in the oral cleaning device into the fluid pump chamber 11 through the fluid input channel 12 and providing an impact water flow through the fluid output channel 13. A drive mechanism is disposed within the grip housing 70 and includes a first drive member 73 adapted to drive the brush head 90 to swing left and right to clean the teeth, and a second drive member adapted to drive the eccentric to rotate about the rotation axis. For example, the first drive member 73 may be a vibration motor for driving the brush head 90 to vibrate, thereby realizing the function of an electric toothbrush. The second drive member 60 may be a servo motor for driving the rotation axis 21 to rotate, thereby driving the eccentric, connecting rod 30, and displacement unit 40 to move, thereby changing the volume of the fluid pump chamber 11 and realizing the function of an oral irrigator. The distance between the second end of the connecting rod 30 and the two extreme positions close to the rotating shaft 21 and away from the rotating shaft 21 during the reciprocating movement is within the range of 2.1mm to 2.6mm, and the volume of the fluid pump chamber 11 is 120mm. 3 Up to 165mm 3 within the range.

[0186] Based on this, the distance between the two extreme positions of the connecting rod 30 is set within a range of 2.1 mm to 2.6 mm. This range is sufficient for the displacement unit 40 to meet the pressure fluctuation requirements within the fluid pump chamber 11. This can correspondingly reduce the space within the housing 10 required to support the movement of the connecting rod 30, thereby reducing the design dimensions of the housing 10 and the size of the device. Utilizing the technical solution of this embodiment, the rotation of the eccentric wheel drives the displacement unit 40 back and forth through the second end of the connecting rod 30, causing the fluid output channel 13 to form a pulsed jet. While ensuring impact force, it also saves liquid consumption, allowing a smaller fluid storage unit to meet liquid consumption requirements. Furthermore, the distance between the two extreme positions of the connecting rod 30 is 2.1 mm to 2.6 mm. This configuration reduces the space within the housing 10 required to support the movement of the connecting rod 30, thereby reducing the size of the housing 10. The second drive member 60 is a brushless motor disposed within the grip housing 70. The rotating shaft 21 is the output shaft of the brushless motor. The speed of the brushless motor is within the range of 3500 mrp to 4500 mrp. The brushless motor has excellent torque characteristics and a wide speed regulation range, so there is no need to set up an additional gear box, which further simplifies the structure and reduces the size of the grip housing 70.

[0187] As shown in FIG3 , the dotted arrows in the figure indicate the effective movement direction of the connecting rod 30 , which means that the connecting rod 30 is required to reciprocate in a first direction and a second direction. The two extreme positions of the connecting rod 30 are located in the first direction and the second direction, respectively. When the connecting rod 30 moves to the extreme position in the first direction, the displacement unit 40 discharges the liquid in the fluid pump chamber 11 . When the connecting rod 30 moves to the extreme position in the second direction, the displacement unit 40 is at its maximum distance from the opposite fluid pump chamber 11 , reducing the pressure in the fluid pump chamber 11 and allowing liquid to enter the fluid pump chamber 11 from the fluid input channel 12 .

[0188] As shown in Figures 3 and 4, the edge of the displacement unit 40 is fixedly set on the side wall of the fluid pump chamber 11, the displacement unit 40 and the second end of the connecting rod 30 can be connected by screws, and the displacement unit 40 can be integrally injection molded with the screws, which simplifies the structure and reduces the difficulty of assembly.

[0189] As shown in Figures 3 and 4, the housing 10 has a cavity for accommodating the eccentric wheel. The bottom of the housing 10 is provided with a second driving member 60. The output shaft of the second driving member 60 extends into the cavity and is coupled to the eccentric wheel to form a rotating shaft 21. The second driving member can drive the eccentric wheel to rotate through the rotating shaft 21. For example, a shaft knurling can be provided on the rotating shaft 21, and the eccentric wheel is pressed onto the shaft knurling. The shaft knurling can increase the friction between the rotating shaft 21 and the eccentric wheel to ensure that the rotating shaft 21 can smoothly drive the eccentric wheel to rotate. A shaft seat is provided in the cavity, and the end of the output shaft of the second driving member 60 can extend into the shaft seat to improve the stability of the output shaft rotation. In addition to providing space for the above components, the cavity also needs to provide a certain amount of movement space for the rotation of the eccentric wheel and the reciprocating motion of the first end of the connecting rod 30. The distance between the two extreme positions of the connecting rod 30 is set to 2.1mm to 2.6mm to limit the size of the movement space in the cavity, and based on this, the overall design size of the housing 10 can be reduced.

[0190] The applicant has demonstrated through a large amount of experimental data that if the distance between the two extreme positions of the connecting rod 30 is less than 2.1 mm, the pumping force will be weakened, and the water flow rate of the pump will be insufficient, which cannot meet the requirements of the fluid impact force; if the distance between the two extreme positions of the connecting rod 30 is greater than 2.6 mm, the design size of the cavity is too large, which cannot meet the requirements of reducing the overall design size of the shell 10. Therefore, the distance between the two extreme positions of the connecting rod 30 is set at 2.1 mm to 2.6 mm, for example, it can be 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm or 2.6 mm.

[0191] In this embodiment, the first end of the connecting rod 30 coincides with the geometric center of the eccentric relative to the rotational center of the eccentric, and the eccentricity of the eccentric is within a range of 1.05 mm to 1.3 mm. When the rotational center of the first end of the connecting rod 30 coincides with the collective center of the eccentric, the travel of the second end of the connecting rod is twice the eccentricity of the eccentric. Setting the eccentricity of the eccentric within a range of 1.05 mm to 1.3 mm ensures that the distance between the two extreme positions of the connecting rod 30 is within a range of 2.1 mm to 2.6 mm.

[0192] As shown in Figures 4 and 5, in this embodiment, the cross-section of the eccentric is configured to be circular, perpendicular to the rotation axis 21. The first end of the connecting rod 30 is provided with a sleeve, the axis of which is parallel to the rotation axis 21 and is disposed outside the eccentric. The eccentric has an axial hole 201 that mates with the rotation axis 21. The eccentric is configured as a circle, and the sleeve can also be configured as a circle, thereby reducing friction between the eccentric and the first end of the connecting rod 30, ensuring that the first end of the connecting rod 30 can perform reciprocating circular motion through the sleeve and the outer edge of the eccentric. With the eccentric rotating 360° around the rotation axis 21 as one complete stroke of the connecting rod 30, the first end of the connecting rod 30 performs reciprocating circular motion, which is more conducive to controlling the distance between the two extreme positions of the connecting rod 30 to be between 2.1 mm and 2.6 mm, thereby ensuring that the displacement unit 40 can provide a stable pressure differential.

[0193] In order to further reduce the friction between the eccentric wheel and the sleeve hole, a bearing 22 can be set between the eccentric wheel and the connecting rod 30. The bearing 22 is sleeved on the eccentric wheel, and the sleeve hole is sleeved on the bearing 22. The bearing 22 can reduce the friction between the eccentric wheel and the connecting rod 30, and prevent the eccentric wheel from driving the connecting rod to rotate coaxially, so as to ensure that the connecting rod 30 can perform a cyclic reciprocating motion in a direction perpendicular to the rotating shaft 21.

[0194] Since the center of mass of the eccentric is not located on the axis of the rotating shaft 21, an unbalanced centrifugal force will be generated during the rotation of the eccentric. The generated unbalanced torque increases the burden on the output shaft of the second drive member 60, increasing the friction resistance of the axle and the heat generation.

[0195] To solve the above problems, as shown in Figures 5, 6 and 7, in this embodiment, a balancing weight 23 is connected to the eccentric wheel. The balancing weight 23 is suitable for increasing the weight at the rotating shaft 21 of the eccentric wheel to balance the torque of the eccentric wheel during rotation. Specifically, the weights of the balancing weight 23 are different at opposite ends. The heavier end is arranged at the top of the shaft hole 201, which extends to the end surface of the balancing weight 23 and passes through the balancing weight 23. The lighter end is arranged at the top of the side opposite to the shaft hole 201. This arrangement can increase the mass of one side of the rotating shaft 21, thereby making the weights of the eccentric wheel on opposite sides of the rotating shaft 21 equal or nearly equal. Then, when the eccentric wheel rotates, the centrifugal force at both ends of the eccentric wheel is equal, solving the problem of unbalanced centrifugal force at both ends of the eccentric wheel, thereby balancing the torque of the output shaft of the second drive member 60, making the rotation of the output shaft of the second drive member 60 more stable, reducing the friction resistance of the axle protrusion, and reducing heat generation. In addition, arranging the balancing weight 23 on the top of the eccentric wheel can avoid motion interference between the balancing weight 23 and the connecting rod 30, thereby avoiding interference with the transmission of the eccentric wheel and the connecting rod 30.

[0196] In one specific implementation of this embodiment, the cross-section of the balancing weight 23 can be symmetrical. The dashed lines in Figures 6 and 7 indicate the axis of symmetry of the balancing weight 23. This configuration avoids introducing new unbalanced forces. Specifically, using the orientation shown in Figure 7 as an example, the balancing weight 23 has two arcuate sides in the left and right directions, with the left arcuate side being shorter than the right arcuate side, and a hypotenuse in the vertical direction, which slopes outward toward the right arc. This makes the right side dimension of the balancing weight 23 larger than the right side dimension. If the density of the balancing weight 23 is uniform, that is, the right side weight of 23 is greater than the left side weight, thereby balancing the centrifugal forces on the left and right sides when the eccentric wheel rotates.

[0197] Of course, the structure of the balancing weight 23 can also be adaptively adjusted by simply increasing the weight at the shaft hole 201 of the eccentric wheel.

[0198] In this embodiment, the eccentric wheel and the balancing weight 23 are integrally formed, which is convenient for production and reduces assembly errors. Fasteners can also be used, such as screws to fix the balancing weight 23 to the eccentric wheel, making it convenient to adjust or replace the balancing weight 23 later.

[0199] In another implementation of this embodiment, the second driving member 60 is a linear motor arranged in the gripping shell 70, and the linkage unit 20 is the output shaft of the linear motor. The stroke of the output shaft is in the range of 2.1 mm to 2.6 mm. The output shaft of the linear motor drives the displacement unit 40 to perform reciprocating motion to provide cyclically increasing and decreasing pressure to the fluid pump chamber 11.

[0200] In this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3Up to 165mm 3 The amount of liquid used per unit time in the fluid output channel 13 is related to the volume of the fluid pump chamber 11. Specifically, the amount of liquid discharged per unit time in the fluid output channel 13 increases with the increase in the volume of the fluid pump chamber 11. When the diameter of the fluid output channel 13 remains unchanged, the impact force of the fluid also increases with the increase in the amount of liquid discharged per unit time. The applicant has conducted a large number of experimental demonstrations and found that when the distance between the two extreme positions of the connecting rod 30 is 2.2mm to 2.4mm, the volume of the fluid pump chamber 11 is 120mm. 3 Up to 165mm 3 If the volume of the fluid pump chamber 11 is less than 120 mm, the pressure of the fluid output channel 13 can meet the requirements of both impact force and liquid conservation. 3 , the liquid flow is too small to meet the impact force requirements; if the volume of the fluid pump chamber 11 is greater than 165mm 3 Although the impact force requirement can be met, the excessive amount of liquid discharged per unit time means that the consumption of the liquid in the fluid storage unit 50 will be accelerated, resulting in the inability to meet the cleaning time requirement and affecting the cleaning effect.

[0201] Further preferably, in this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm 3 In the case where the distance between the two extreme positions of the connecting rod 30 during the reciprocating movement is within the range of , the distance between the two extreme positions of the connecting rod 30 during the reciprocating movement is selected to be 2.2 mm.

[0202] For example, the volume of the fluid pump chamber 11 may be 120 mm 3 , 121mm 3 , 122mm 3 , 123mm 3 ...or 130mm 3 As shown in Figure 3, when the second end of the connecting rod 30 moves to the extreme position in the first direction, the displacement unit 40 can completely fit against the side wall of the fluid pump chamber 11, thereby completely draining the liquid in the fluid pump chamber 11. If the extreme position is greater than 2.2 mm, the displacement unit 40 will interfere with the side wall of the fluid pump chamber 11 during the movement of the second end of the connecting rod 30 to the extreme position in the first direction.

[0203] Further preferably, in this embodiment, the volume of the fluid pump chamber is 155mm 3 Up to 165mm 3 In the case that the range is within the range, the distance between the two extreme positions of the connecting rod during the reciprocating movement is selected to be 2.4mm.

[0204] For example, the volume of the fluid pump chamber 11 may be 155 mm3 , 156mm 3 , 157mm 3 , 158mm 3 ...or 165mm 3 As shown in Figure 3, when the second end of the connecting rod 30 moves to the extreme position in the first direction, the displacement unit 40 can completely fit against the side wall of the fluid pump chamber 11, thereby completely draining the liquid in the fluid pump chamber 11. If the extreme position is less than 2.4 mm, a gap will exist between the displacement unit 40 and the side wall of the fluid pump chamber 11 when the second end of the connecting rod 30 moves to the extreme position in the first direction, reducing the operating efficiency of the fluid pump chamber 11.

[0205] In this embodiment, by optimizing various parameters of the fluid pumping unit, the fluid pumping unit can be made more liquid-saving while ensuring the cleaning power, so that the size of the fluid storage unit in the oral cleaning device can be made smaller, thereby solving the contradiction between the product size and cleaning power of the oral irrigator in the prior art.

[0206] The above is an explanation of the principle of movement of the various components of the fluid pumping unit in this embodiment. The following is a detailed introduction to the basis for determining the values ​​of various parameters in the fluid pumping unit in this embodiment.

[0207] 1. The distance between the two extreme positions of the connecting rod 30 during reciprocating motion

[0208] To change the size of the oral cleaning appliance, it is necessary to give priority to the large-volume components in the oral cleaning appliance. Currently, the volume of the fluid pumping unit and the volume of the fluid storage unit have a direct impact on the size of the oral cleaning appliance. The fluid pumping unit not only needs to provide a storage space for each moving part, but also needs to provide a movement space for each moving part. Therefore, the connecting rod 30 can be improved from the perspective of the storage space and the movement space. In order to select the optimal distance range between the two extreme positions in the reciprocating motion of the connecting rod 30, while controlling other parameters unchanged and only changing the distance between the two extreme positions in the reciprocating motion of the connecting rod 30, the applicant obtained the following four groups of experimental data through experiments, refer to Figure 8:

[0209] Sample 1: The distance is 2.0 mm, the impact force is 0.041 N to 0.062 N, and the time required to pump out 200 ml of liquid is 75 seconds to 89 seconds.

[0210] Sample 2: The distance is 2.2mm, the impact force is 0.90N to 0.98N, and the time required to draw out 200ml of liquid is 54 seconds to 68 seconds.

[0211] Sample 3: The distance is 2.4mm, the impact force is 0.107N to 0.114N, and the time required to draw out 200ml of liquid is 47 seconds to 49 seconds.

[0212] Sample 4: The distance is 2.6mm, the impact force is 0.127N to 0.130N, and the time required to draw out 200ml of liquid is 40 seconds to 43 seconds.

[0213] A greater impact force indicates stronger cleaning power, while a smaller impact force indicates weaker cleaning power. A shorter time to draw out 200ml of liquid means more liquid is used, while a longer time means less liquid. The experimental data above shows that greater cleaning power results in greater liquid consumption, so a balance needs to be struck between these two conditions.

[0214] Furthermore, as the distance between the two extreme positions of the connecting rod 30 increases during its reciprocating motion, the concave-convex deformation capability of the displacement unit 40 also increases, thereby increasing the inflow and outflow rates of the fluid pump chamber 11. The greater the outflow rate, the greater the impact force in the fluid output channel 13. The applicant has experimentally determined that an impact force ≥ 0.07 N satisfies the requirements for oral hygiene. Therefore, a standard impact force ≥ 0.07 N can be used as a basis for subsequent experiments to determine other design parameters.

[0215] In sample 1, although it takes a long time to draw out 200ml of liquid, which can achieve the purpose of saving liquid, the cleaning power does not meet the requirements and cannot meet the needs of oral cleaning, so it is discarded.

[0216] In sample 4, although the impact force is large, the time required to pump out 200ml of liquid is too short, and it is likely that it cannot meet the cleaning time once, so it is eliminated.

[0217] In samples 2 and 3, the impact force was sufficient and the time required to pump out 200 ml of liquid was relatively reasonable, so they were retained.

[0218] In summary, in this embodiment, the two extreme positions of the connecting rod 30 during the reciprocating motion are ultimately determined to be between 2.2 mm and 2.4 mm. Within this range, the liquid discharge volume per unit time can be satisfied, the standard impact force requirement can be met, and the liquid discharge volume per unit time can be controlled within a certain range, without increasing the volume of the fluid storage unit 50. Specifically, if the distance between the two extreme positions of the connecting rod 30 is less than 2.2 mm, the liquid flow rate will be insufficient and the fluid impact force requirement cannot be met. If the distance between the two extreme positions of the connecting rod 30 is greater than 2.4 mm, the design size of the cavity is too large, which cannot meet the requirement of reducing the overall design size of the housing 10. At the same time, the liquid discharge volume per unit time will increase, and a larger volume of the fluid storage unit 50 will be required to provide sufficient liquid storage capacity.

[0219] 2. Volume Range of Fluid Pump Chamber 11

[0220] The volume of the fluid pump chamber 11 in this embodiment is related to the flow rate of liquid discharged by the displacement unit 40 in one complete concave-convex deformation. Therefore, the volume of the fluid pump chamber 11 must satisfy both sufficient flow rate per unit time and the deformation stroke of the displacement unit 40. The flow rate per unit time of the fluid pump chamber 11 is related to the rotation speed of the second drive member. In this embodiment, the rotation speed n of the second drive member is preferably 3500mrp to 4500mrp. If the rotation speed n of the second drive member is less than 3500mrp, it cannot be guaranteed that the calculated flow rate per unit time of the fluid pump chamber 11 meets the requirements. If the rotation speed n of the second drive member is greater than 4500mrp, it will cause excessive noise. The flow rate per unit time of the fluid pump chamber 11 can be calculated by the following formula: Q 流体泵腔 =nv. Among them, Q 流体泵腔 is the flow rate per unit time of the fluid pump chamber 11. n is the speed of the second drive member, that is, the speed of the eccentric wheel. v is the volume of the fluid pump chamber 11. From the above formula, the calculated flow rate per unit time of the fluid pump chamber 11 can be calculated. When the diameter of the fluid output channel 13 remains unchanged, the formula: F = 10.2ρQ 流体泵腔 2 The jet impact force is calculated using the equation: / A, where F is the jet impact force and ρ is the density of the jet medium, which can be the liquid mentioned above. A can be the cross-sectional area of ​​the jet pipeline, which includes at least the cross-sectional area of ​​the fluid output channel 13 and the nozzle used for oral cleaning.

[0221] Refer to the experimental data shown in Figure 8:

[0222] Sample 1, distance is 2.0mm, volume of fluid pump chamber 11 is 120mm 3 Up to 130mm 3 Although it takes a long time to pump 200ml of liquid, the impact force is only 0.041N to 0.062N, which does not meet the standard impact force requirements and is therefore rejected. Comparing Sample 1 and Sample 2, it can be found that although the volume of the fluid pump chamber 11 is unchanged, the smaller distance in Sample 1 cannot ensure that the displacement unit 40 maintains high working efficiency.

[0223] Sample 4, distance is 2.6mm, volume of fluid pump chamber 11 is 155mm 3 Up to 165mm 3 Although it can meet the standard requirements of impact force, compared with sample 3, sample 3 can save more liquid while meeting the impact force requirements, so sample 4 is eliminated.

[0224] Figure 9 is a schematic diagram showing the relationship between the impact force and the distance between the two extreme positions of the connecting rod. The dotted line corresponds to the minimum impact force, and the solid line corresponds to the maximum impact force. The analysis is as follows:

[0225] It should be noted that, considering that the utilization rate of the fluid pump chamber 11 is restricted by the limit position of the connecting rod 30 and the volume of the fluid pump chamber 11, it is necessary to ensure that the utilization rate of the fluid pump chamber 11 is maintained at a high level as much as possible. Among them, the main influencing factor is the following standard: during the process of the connecting rod 30 completing a stroke, whether the displacement unit 40 can be completely attached to the side wall when it moves to the limit distance in the direction of the fluid pump chamber 11. Based on this, the following four sets of data are obtained to ensure that the utilization rate of the fluid pump chamber 11 is at a high level. For example, the distance between the two limit positions of the connecting rod 30 is 2.0 mm, and the volume of the fluid pump chamber is 120 mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.2mm, and the volume of the fluid pump chamber is 120mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.4mm, and the volume of the fluid pump chamber is 155mm 3 Up to 165mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.6mm, and the volume of the fluid pump chamber is 155mm 3 Up to 165mm 3 .

[0226] As can be seen from the dotted lines in Figure 9, as the distance between the two extreme positions of the connecting rod 30 increases, the minimum impact force does not increase proportionally. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the minimum impact force shows a first increasing trend. When it is in the range of 2.2mm to 2.4, the change in the minimum impact force shows a first decreasing trend. When it is in the range of 2.4mm to 2.6, the change in the minimum impact force shows a second increasing trend. Due to the differences in the volume of the fluid pump chamber 11 in the above data, it can be divided into the following three situations:

[0227] The first case is that the volume of the fluid pump chamber 11 is 120mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod is in the range of 2.0mm to 2.2mm. As the distance between the two extreme positions of the connecting rod 30 increases, the impact force also increases. This is because the increase in the distance between the two extreme positions of the connecting rod 30 directly affects the utilization rate of the fluid pump chamber 11, that is, the stroke of the displacement unit 40 is increased, thereby increasing the liquid inlet capacity of the fluid pump chamber 11, which also directly affects the flow rate of the fluid pump chamber 11 per unit time, thereby increasing the impact force.

[0228] The second case is that the volume of the fluid pump chamber 11 is 155mm 3 Up to 165mm 3 Within the range, the distance between the two extreme positions of the connecting rod 30 is in the range of 2.4mm to 2.6mm. As the distance between the two extreme positions of the connecting rod 30 increases, the impact force also increases. This is because the increase in the distance between the two extreme positions of the connecting rod 30 directly affects the utilization rate of the fluid pump chamber 11, that is, the stroke of the displacement unit 40 is increased, thereby increasing the liquid inlet capacity of the fluid pump chamber 11, which also directly affects the flow rate of the fluid pump chamber 11 per unit time, thereby increasing the impact force.

[0229] In the third case, the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 Up to 165mm 3 Within the range, the distance between the two extreme positions of the connecting rod 30 is 2.4 mm. From the changing trend, although the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 increase, the minimum impact force decreases. Therefore, it is confirmed that the impact force does not tend to increase proportionally with the increase of the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30.

[0230] From the comparison between Case 1 and Case 2, when the volume of the fluid pump chamber 11 is the same, as the distance between the two extreme positions of the connecting rod 30 increases, the utilization rate of the fluid pump chamber 11 gradually increases, the amount of liquid discharged increases, and the impact force also gradually increases, and the first growth trend is smaller than the second growth trend. This means that when the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 are large, the impact force increases more with the increase in the distance between the two extreme positions of the connecting rod 30, making it easier to meet the requirement of a larger impact force. This means that when the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 are small, it is easier to meet the requirement of a stable impact force. From Case 3, in addition to the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11, there are other factors that affect the impact force.

[0231] As can be seen from the solid line in Figure 9, as the distance between the two extreme positions of the connecting rod 30 increases, the maximum impact force does not increase proportionally. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the maximum impact force shows the third growth trend. In the range of 2.2mm to 2.4, the change in the maximum impact force shows the fourth growth trend. In the range of 2.4mm to 2.6, the change in the maximum impact force shows the fifth growth trend. There is a clear difference between the third growth trend, the fourth growth trend and the fifth growth trend. Figure 10 is a schematic diagram of the relationship between the pumping time and the distance between the two extreme positions of the connecting rod, where the dotted line corresponds to the shortest time and the solid line corresponds to the longest time. The analysis is as follows:

[0232] As can be seen from the dotted lines in Figure 10, as the distance between the two extreme positions of the connecting rod 30 increases, the shortest time does not show a proportional decreasing trend. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the shortest time shows a first downward trend. When it is in the range of 2.2mm to 2.4mm, the change in the shortest time shows a first upward trend. When it is in the range of 2.4mm to 2.6mm, the change in the shortest time shows a second downward trend. The shorter the pumping time, the greater the actual flow rate of the fluid pump chamber 11 per unit time, and the more liquid is consumed. It can be divided into the following three situations:

[0233] The first case is that the volume of the fluid pump chamber 11 is 120mm 3 Up to 130mm 3 The distance between the two extreme positions of the connecting rod is in the range of 2.0mm to 2.2mm. As the distance between the two extreme positions of the connecting rod 30 increases, the shortest time becomes shorter, which corresponds to the analysis results of Figure 9 above. The impact force also increases. It is not difficult to judge that as the distance between the two extreme positions of the connecting rod 30 increases, the flow rate per unit time in the fluid pump chamber 11 will also increase, thereby increasing the impact force, which confirms the above analysis.

[0234] The second case is that the volume of the fluid pump chamber 11 is 155mm 3 Up to 165mm 3 Within the range of , the distance between the two extreme positions of the connecting rod 30 is in the range of 2.4mm to 2.6mm. As the distance between the two extreme positions of the connecting rod 30 increases, the shortest time becomes shorter. Corresponding to the analysis of Figure 9 above, the impact force also increases. It is not difficult to judge that as the distance between the two extreme positions of the connecting rod 30 increases, the flow rate per unit time of the fluid pump chamber 11 will also increase, thereby increasing the impact force, which confirms the above analysis.

[0235] In the third case, the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm3 The distance between the two extreme positions of the connecting rod 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 Up to 165mm 3 Within the range, the distance between the two extreme positions of the connecting rod 30 is 2.4 mm. From the changing trend, although the volume of the fluid pump chamber 11 and the distance between the two extreme positions of the connecting rod 30 increase, the shortest time becomes longer, corresponding to the analysis of Figure 9 above, the minimum impact force decreases, which confirms the above analysis.

[0236] Judging from the solid line in Figure 10, as the distance between the two extreme positions of the connecting rod 30 becomes farther, the maximum time does not show a trend of decreasing in equal proportion. When the distance between the two extreme positions of the connecting rod 30 is in the range of 2.0mm to 2.2mm, the change in the maximum time shows the third downward trend. When it is in the range of 2.2mm to 2.4, the change in the maximum time shows the fourth downward trend. When it is in the range of 2.4mm to 2.6, the change in the maximum time shows the fifth downward trend. There are obvious differences between the third downward trend, the fourth downward trend and the fifth downward trend.

[0237] Through the above two analysis processes, it can be seen that the water output per unit time of the fluid pump chamber 11 has become a factor affecting the impact force. And from an overall perspective, when the volume of the fluid pump chamber 11 is in a small range, it is necessary to ensure that the distance between the two extreme positions of the connecting rod 30 meets the requirements to ensure that the fluid pump chamber 11 has sufficient efficiency. Moreover, the volume of the fluid pump chamber 11 cannot be too small to ensure sufficient liquid output to meet the impact force requirements. When the volume of the fluid pump chamber 11 is in a large range, it is necessary to reasonably control the distance between the two extreme positions of the connecting rod 30 to control the actual flow rate of the fluid pump chamber 11 per unit time to meet the requirement of saving liquid.

[0238] Therefore, if the volume of the fluid pump chamber 11 is less than 120 mm 3 , it will lead to insufficient liquid discharge, and without changing the liquid discharge cross-sectional area, it will not be able to meet the standard requirements of the impact force; if the volume of the fluid pump chamber 11 is greater than 165mm 3 , will result in excessive liquid output per unit time. Although it can meet the standard requirements of impact force, it will accelerate the consumption of liquid in the fluid storage unit 50. Increasing the volume of the fluid storage unit 50 can meet the liquid demand, but it will undoubtedly increase the overall size of the oral cleaning appliance. Therefore, the volume of the fluid pump chamber 11 is 120mm 3 Up to 165mm 3 The standard requirements for impact force can be met within the range, and the flow rate of the fluid pump chamber 11 per unit time can be controlled, thereby achieving the purpose of saving liquid and reducing the volume of the fluid storage unit 50.

[0239] Since the distance between the two extreme deformation strokes of the displacement unit 40 corresponds to the distance between the two extreme positions of the connecting rod 30 during the movement, under the premise of ensuring the maximum efficiency of the fluid pump chamber 11, it can be specifically divided into at least the following two situations:

[0240] The first case is that when the distance between the two extreme positions of the connecting rod 30 during the reciprocating motion is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 Up to 130mm 3 As shown in FIG3 , when the second end of the connecting rod 30 moves to the extreme position in the first direction, the displacement unit 40 can be completely attached to the side wall of the fluid pump chamber 11, thereby completely discharging the liquid in the fluid pump chamber 11 to achieve the maximum efficiency of the fluid pump chamber 11. If the volume of the fluid pump chamber 11 is greater than 130mm 3 When the second end of the connecting rod 30 moves to the extreme position in the first direction, a gap will exist between the displacement unit 40 and the side wall of the fluid pump chamber 11, thereby reducing the efficiency of the fluid pump chamber 11.

[0241] The second case is that when the distance between the two extreme positions of the connecting rod 30 during the reciprocating motion is 2.4 mm, the volume of the fluid pump chamber 11 is 155 mm. 3 Up to 165mm 3 As shown in FIG3 , when the second end of the connecting rod 30 moves to the extreme position in the first direction, the displacement unit 40 can be completely attached to the side wall of the fluid pump chamber 11, thereby completely discharging the liquid in the fluid pump chamber 11 to achieve the maximum efficiency of the fluid pump chamber 11. If the volume of the fluid pump chamber 11 is less than 155mm 3 , it may cause the side wall of the fluid pump chamber 11 to interfere with the displacement unit 40, resulting in the displacement unit 40 being unable to complete the deformation stroke of the limit distance of 2.4 mm.

[0242] In this embodiment, the ratio of the calculated flow rate per unit time of the fluid pump chamber to the actual flow rate per unit time of the fluid output channel can satisfy the following relationship: K = Q 流体泵腔 / Q 流体输出通道 Where K is the ratio of the calculated flow rate per unit time of the fluid pump cavity to the actual flow rate per unit time of the fluid output channel. When K is within the range of 2.93≦K≦3.75, Q 流体泵腔 Calculate the flow rate per unit time of the fluid pump cavity, Q 流体输出通道 is the actual flow rate per unit time of the fluid output channel, that is, the actual flow rate per unit time can be determined by measuring the actual liquid outflow rate of the fluid output channel 13.

[0243] Through extensive experimental data, the applicant discovered that the smaller the K value, the more liquid flows out of fluid output channel 13 per unit time, resulting in a greater impact force. A larger K value, however, results in less liquid flowing out of fluid output channel 13 per unit time, resulting in a smaller impact force. Based on standard requirements for impact force, when the K value is greater than 3.75, the impact force of fluid output channel 13 fails to meet the standard requirements. When the K value is less than 2.93, while the impact force requirement can be met, the actual flow rate per unit time increases, resulting in excessive liquid consumption and failing to meet the requirement for liquid conservation.

[0244] Furthermore, Q 流体泵腔 and Q 流体输出通道 The difference is caused by the pressure loss caused by the resistance along the liquid in the liquid pipeline. For example, in addition to the fluid input channel 12 and fluid output channel 13 introduced in this embodiment, the liquid will pass through elbows, tees, reducers, valves and other components after leaving the fluid storage unit 50 or before entering the nozzle 80. The flow state of the liquid will change dramatically, that is, turning, acceleration, collision, vortex, deformation, etc. will occur, which will cause pressure loss, making it impossible to pump the liquid into the fluid pump chamber 11 according to the calculated data, and it is also impossible to completely discharge the liquid in the fluid pump chamber 11 according to the calculated discharge volume. During the experiment, the actual discharge volume per unit time can be received by an external container to record the data.

[0245] 3. Inner Diameter Range of Fluid Input Channel 12

[0246] The principle of replenishing liquid in the fluid pump chamber 11 is to use negative pressure to pump liquid from the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12. The inner diameter of the fluid input channel 12 affects the liquid's resistance along the flow path. Through extensive experimental data, the applicant has found that the smaller the inner diameter of the fluid input channel 12, the greater the liquid's resistance along the flow path, the less liquid enters the fluid pump chamber 11, the smaller the actual flow rate of the fluid output channel 13, and the smaller the fluid's impact force. The larger the inner diameter of the fluid input channel 12, the smaller the liquid's resistance along the flow path, the more liquid enters the fluid pump chamber 11, the greater the actual flow rate of the fluid output channel 13, and the greater the fluid's impact force.

[0247] Refer to the experimental data shown in Figure 8:

[0248] Sample 2: The distance is 2.2 mm, and the volume of the fluid pump chamber 11 is 120 mm 3 Up to 130mm 3. When the inner diameter of the fluid input channel 12 is 2.0mm, the actual flow rate per unit time is 174ml / min, and the impact force is 0.067N; when the inner diameter of the fluid input channel 12 is 2.5mm, the actual flow rate per unit time is 182ml / min, and the impact force is 0.067N; when the inner diameter of the fluid input channel 12 is 3.0mm, the actual flow rate per unit time is 235ml / min, and the impact force is 0.094N. From the above data, it can be seen that as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time will also increase, and the impact force is also increasing. Although the impact force is 0.067N when the inner diameter of the fluid input channel 12 is 2.0mm and 2.5mm, which is 0.003N different from the standard impact force, the impact of 0.003N on the cleaning effect can be ignored in actual use.

[0249] Sample 3: The distance is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 Up to 165mm 3 When the inner diameter of the fluid input channel 12 is 2.0 mm, the actual flow rate per unit time is 154 ml / min, and the impact force is 0.06 N. When the inner diameter of the fluid input channel 12 is 2.5 mm, the actual flow rate per unit time is 185 ml / min, and the impact force is 0.072 N. When the inner diameter of the fluid input channel 12 is 3.0 mm, the actual flow rate per unit time is 286 ml / min, and the impact force is 0.104 N. From the above data, it can be seen that as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time also increases, and the impact force also increases.

[0250] FIG11 is a schematic diagram showing the relationship between the impact force and the inner diameter of the fluid input channel. The solid line corresponds to the experimental data of sample 2, and the dotted line corresponds to the experimental data of sample 3. The analysis is as follows:

[0251] As can be seen from the solid line corresponding to Sample 2, when the inner diameter of the fluid input channel 12 increases, the impact force also increases, and the impact force does not increase proportionally according to the coefficient. For example, when the inner diameter of the fluid input channel 12 is between 2.0 mm and 2.5 mm, the impact force hardly changes. However, in the range of 2.5 mm to 3.0 mm, the impact force increases sharply. This is because there are many factors that restrict the actual flow rate of the fluid input channel 12, such as the inner diameter of the fluid input channel 12, the distance between the two extreme positions of the connecting rod 30, the volume of the fluid pump chamber 11, the rotational speed of the second drive member, etc. This embodiment takes the change of the inner diameter of the fluid input channel 12 as an example. When the inner diameter of the fluid input channel 12 changes, the longitudinal resistance of the fluid input channel 12 also decreases. Therefore, this sudden increase trend only occurs after the longitudinal resistance of the fluid input channel 12 decreases to a certain threshold. Obviously, due to the other factors of Sample 2, it is impossible to effectively overcome the limitation of the longitudinal resistance of the fluid input channel 12 below 2.5 mm on the impact force. Therefore, the distance between the two extreme positions of the connecting rod 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 120 mm. 3 Up to 130mm 3 , the inner diameter of the fluid input channel 12 can be preferably set to be greater than 2.5 mm.

[0252] It can be seen from the dotted line corresponding to sample three that when the inner diameter of the fluid input channel 12 increases, the impact force can also increase, and the change trend of the impact force does not increase proportionally according to the coefficient. For example, the inner diameter of the fluid input channel 12 shows a first trend in the range of 2.0mm to 2.5mm, and the fluid input channel 12 shows a second trend in the range of 2.5mm to 3.0mm. It is not difficult to find that the growth rate of the second trend is greater than the growth rate of the first trend. Therefore, it can be found that when the inner diameter of the fluid input channel 12 is less than 2.5mm, the growth rate of the impact force is small, and when the inner diameter of the fluid input channel 12 is greater than 2.5mm, the growth rate of the impact force is large. In addition, the distance between the two extreme positions of the connecting rod 30 of sample three is 2.4mm, and the volume of the fluid pump chamber 11 is 155mm. 3 Up to 165mm 3 , which can overcome the resistance along the fluid input channel 12 below 2.5 mm, so under the parameters of the connecting rod 30 and the fluid pump chamber 11 of sample three, there is no need to consider the resistance along the fluid input channel 12.

[0253] From the comparison of the solid line corresponding to sample 2 and the dotted line corresponding to sample 3 in Figure 11, it can be seen that, under the same inner diameter of the fluid input channel 12, from the perspective of the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11, although the two data of sample 3 are both greater than the two data of sample 2, when the inner diameter of the fluid input channel 12 is in the range of 2.0mm to 2.5mm, the impact force corresponding to sample 3 is smaller than the impact force corresponding to sample 2. Therefore, it is not the case that under the same inner diameter of the fluid input channel 12, the impact force of sample 3 is always greater than the impact force of sample 2. That is, under the same inner diameter of the fluid input channel 12, the increase in the values ​​of the above two data does not increase in proportion to the coefficient. Therefore, it is necessary to reasonably select the inner diameter of the fluid input channel 12 corresponding to samples 2 and 3 to meet the impact force requirements.

[0254] For example, as can be seen from FIG11 , only when the inner diameter of the fluid input channel 12 is greater than 2.5 mm can the impact force of sample 2 gradually meet the basic requirements of the impact force. Therefore, without considering other variables, the inner diameter of the fluid input channel 12 corresponding to sample 2 is preferably greater than 2.5 mm.

[0255] FIG12 is a schematic diagram showing the relationship between the flow rate per unit time of the fluid pump cavity and the inner diameter of the fluid input channel. The solid line corresponds to the experimental data of sample 2, and the dotted line corresponds to the experimental data of sample 3. The analysis is as follows:

[0256] From the solid line corresponding to Sample 2, it can be seen that when the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pump chamber 11 can also increase, and the change trend of the flow rate per unit time of the fluid pump chamber 11 does not increase proportionally according to the coefficient. For example, when the inner diameter of the fluid input channel 12 is in the range of 2.0mm to 2.5mm, the flow rate per unit time of the fluid pump chamber 11 hardly changes. However, in the range of 2.5mm to 3.0mm, the flow rate per unit time of the fluid pump chamber 11 shows a trend of sudden increase. Therefore, it is not difficult to see that although the resistance along the fluid input channel 12 decreases when the inner diameter of the fluid input channel 12 changes, this sudden increase trend will only appear after the resistance along the fluid input channel 12 decreases to a certain threshold. This also confirms the conclusion of the analysis of Figure 11. Obviously, under the constraints of other factors in Sample 2, it is impossible to effectively overcome the limitation of the impact force on the resistance along the fluid input channel 12 below the inner diameter of 2.5mm. Therefore, when the distance between the two extreme positions of the connecting rod 30 is 2.2mm, the volume of the fluid pump chamber 11 is 120mm. 3 Up to 130mm 3 , the inner diameter of the fluid input channel 12 can be preferably set to be greater than 2.5 mm.

[0257] From the dotted line corresponding to sample three, it can be seen that when the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pump chamber 11 can also increase, and the change trend of the flow rate per unit time of the fluid pump chamber 11 does not increase proportionally according to the coefficient. For example, the inner diameter of the fluid input channel 12 shows a first trend in the range of 2.0mm to 2.5mm, and the fluid input channel 12 shows a second trend in the range of 2.5mm to 3.0mm. It is not difficult to find that the growth rate of the second trend is greater than the growth rate of the first trend. Therefore, it can be found that when the inner diameter of the fluid input channel 12 is less than 2.5mm, the growth rate of the flow rate per unit time of the fluid pump chamber 11 is small, and when the inner diameter of the fluid input channel 12 is greater than 2.5mm, the growth rate of the flow rate per unit time of the fluid pump chamber 11 is large. It can be seen that there is a corresponding relationship between the flow rate per unit time of the fluid pump chamber 11 and the impact force. Moreover, the distance between the two extreme positions of the connecting rod 30 of sample three is 2.4mm, and the volume of the fluid pump chamber 11 is 155mm. 3 Up to 165mm 3 , the flow rate per unit time of the fluid pump chamber 11 of sample three can still show an increasing trend, which confirms the analysis conclusion of Figure 11. The parameters of the fluid pump chamber 11 and the connecting rod 30 of sample three can overcome the along-the-path resistance of the fluid input channel 12 below 2.5 mm. Therefore, under the parameters of the connecting rod 30 and the fluid pump chamber 11 of sample three, there is no need to consider the along-the-path resistance of the fluid input channel 12.

[0258] From the comparison of the solid line corresponding to sample 2 and the dotted line corresponding to sample 3 in Figure 12, it can be seen that under the same inner diameter of the fluid input channel 12, from the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11, although the two data of sample 3 are greater than the two data of sample 2, when the inner diameter of the fluid input channel 12 is in the range of 2.0mm to 2.5mm, the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 3 is less than the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 2, which confirms the analysis conclusion in Figure 11. Therefore, it is necessary to reasonably select the inner diameters of the fluid input channels 12 corresponding to samples 2 and 3 to meet the requirements of the flow rate and impact force per unit time of the fluid pump chamber 11.

[0259] Therefore, the inner diameter of the fluid input channel 12 needs to be reasonably selected according to the distance between the two extreme positions of the connecting rod 30 and the volume of the fluid pump chamber 11 to meet the standard requirements of the impact force.

[0260] Optionally, the inner diameter of the fluid input channel 12 is within the range of 2.0 mm to 3.0 mm. For example, the inner diameter of the fluid input channel 12 can be 2.0 mm, 2.1 mm, 2.2 mm... or 3.0 mm. The above inner diameters of the fluid input channel 12 can all meet the requirements of the impact force, and at the same time, the actual flow rate per unit time of the fluid output channel 13 can be controlled to achieve the purpose of saving liquid. If the inner diameter of the fluid input channel 12 is less than 2.0 mm, the actual flow rate per unit time of the fluid output channel 13 will be too small, and it will not be able to meet the standard requirements of the impact force; if the inner diameter of the fluid input channel 12 is greater than 3.0 mm, although it can meet the standard requirements of the impact force, it will cause the actual flow rate per unit time of the fluid output channel 13 to be large, and the purpose of saving liquid will not be achieved.

[0261] Preferably, the inner diameter of the fluid input channel is in the range of 2.5 mm to 3.0 mm. For example, the inner diameter of the fluid input channel 12 can be 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, or 3.0 mm. The inner diameters of the fluid input channel 12 can meet the optimal cleaning requirements while saving liquid, thereby improving the cleaning effect.

[0262] In this embodiment, the diameter of the fluid output hole of the nozzle is in the range of 0.6 mm to 0.65 mm. For example, the diameter of the fluid output hole of the nozzle can be 0.6 mm, 0.61 mm, 0.62 mm, 0.63 mm, 0.64 mm or 0.65 mm.

[0263] In this embodiment, the rotation speed of the second driving member 60 is in the range of 3500 rpm to 4500 rpm. Within this range, the flow rate of the fluid pump chamber 11 per unit time can be guaranteed. According to the formula Q 流体泵腔 =nv,Q 流体泵腔 Within the range of 542ml / min to 693ml / min, the K value can be satisfied within the range of 2.93 to 3.75. It should be noted that due to the existence of resistance along the way, the calculated flow rate per unit time of the fluid pump chamber 11 and the flow rate per unit time of the nozzle 80 are in a certain proportional relationship. The larger the K value, the smaller the flow rate per unit time of the nozzle, and the more liquid can be saved.

[0264] In this embodiment, the volume of the fluid storage unit 50 is in the range of 50 ml to 200 ml. Within this range, the amount of liquid stored in the fluid storage unit 50 is sufficient to meet the requirements for teeth cleaning.

[0265] In this embodiment, the capacity of the fluid storage unit 50 is in the range of 50 ml to 90 ml. The capacity of the fluid storage unit 50 is related to the volume. Reducing the volume of the fluid storage unit 50 is beneficial to reducing the size of the grip housing 70.

[0266] In one implementation of this embodiment, the displacement unit 40 is a diaphragm. The edge of the diaphragm is attached to the side wall of the housing 10 in the second direction, so the end surface of the diaphragm facing the first direction and the side wall of the housing 10 in the first direction enclose and seal to form a sealed space with variable volume, which is the fluid pump chamber 11. The end surface of the diaphragm facing the second direction is connected to the linkage unit 20, so that the diaphragm can be deformed concavely and convexly under the drive of the linkage unit 20 to change the volume of the fluid pump chamber 11, and then change the pressure of the fluid pump chamber 11. Referring to Figure 3, taking the linkage unit 20 as an example of the connection between the connecting rod 30 and the eccentric wheel:

[0267] The eccentric is located in a second direction within the housing 10, opposite to the first direction of the diaphragm. The eccentric has a rotation axis 21 offset from its geometric center. The eccentric is adapted to rotate about this axis 21. The axis 21 extends through the eccentric and along its rotational axis, which is parallel to and non-coincident with the eccentric's central axis. The geometric center of the eccentric is the center of its geometric shape. Therefore, when the eccentric rotates about the axis 21, it performs an eccentric rotational motion.

[0268] The connecting rod 30 is located between the diaphragm and the eccentric. The first end of the connecting rod 30 is rotatably connected to the eccentric so that when the eccentric rotates, the connecting rod 30 is driven to reciprocate in a direction perpendicular to the rotation axis 21. The second end of the connecting rod 30 extends in a direction away from the rotation axis 21, as shown in the first and second directions in Figure 3, and the diaphragm reciprocates in the first and second directions. The first end of the connecting rod 30 can serve as a power input end, and the first end of the connecting rod 30 can rotate about the rotation center under the drive of the eccentric. The second end opposite the first end can serve as a power output end, and the second end of the connecting rod 30 can reciprocate perpendicular to the rotation axis 21.

[0269] The diaphragm is connected to the second end of the connecting rod 30 and extends into the fluid pump chamber 11. The plane in the fluid pump chamber 11 on which the diaphragm acts is arranged parallel to the rotating shaft 21. During the reciprocating movement of the connecting rod 30, the diaphragm cyclically increases and decreases the volume in the fluid pump chamber 11, so that the liquid in the fluid storage unit 50 in the oral cleaning appliance is pumped into the fluid pump chamber 11 through the fluid input channel 12, and the impact fluid is provided through the fluid output channel 13.

[0270] Specifically, a sealed space is formed by the diaphragm, the sidewalls of the fluid pump chamber 11, the one-way valve of the fluid input channel 12, and the one-way valve of the fluid output channel 13. The concave-convex deformation of the diaphragm can change the volume of the sealed space, and the pressure within the fluid pump chamber 11 will increase or decrease accordingly. When the pressure within the fluid pump chamber 11 decreases, liquid is pumped from the fluid storage unit 50 through the fluid input channel 12 into the fluid pump chamber 11 under the action of negative pressure. When the pressure within the fluid pump chamber 11 increases, the liquid is discharged from the fluid pump chamber 11 through the fluid output channel 13 to form a percussive fluid. Since the fluid pump chamber 11 needs to suck in the liquid and then discharge it, a discontinuous pulse jet is formed in the fluid output channel 13. The water hammer pressure of the pulse jet is greater than the stagnation pressure of the continuous jet. In principle, the pulse water flow can use the water hammer effect to generate huge transient energy, thereby increasing the impact force of the impact water flow, thereby improving the cleaning effect. Compared with continuous water flow, the pulse water flow can save liquid, which can reduce the volume of the fluid storage unit and reduce the size of the fuselage.

[0271] Based on this, the distance between the two extreme positions of the connecting rod 30 is set within the range of 2.1mm to 2.6mm. This range is sufficient to allow the diaphragm to effectively deform concavely and convexly to meet the pressure change requirements in the fluid pump chamber 11. Then, the space in the housing 10 used to support the movement of the connecting rod 30 can be reduced accordingly, thereby reducing the design size of the housing 10 and the size of the fuselage. Using the technical solution of this embodiment, the rotation of the eccentric wheel drives the diaphragm to reciprocate through the second end of the connecting rod 30, so that the fluid output channel 13 forms a pulse jet. While ensuring the impact force, it can also save the amount of liquid used, and a smaller volume of fluid storage unit can be used to meet the liquid volume requirements. At the same time, the distance between the two extreme positions of the connecting rod 30 is 2.1mm to 2.6mm. This setting reduces the space in the housing 10 that supports the movement of the connecting rod 30 and reduces the size of the housing 10.

[0272] In another embodiment of the present invention, the displacement unit 40 is a piston. Unlike the previous embodiment, the movement of the diaphragm is concave-convex deformation. Therefore, the inner wall of the housing 10 located in the first direction of the diaphragm needs to be set to a corresponding concave surface, while the movement of the piston is to slide along the inner wall of the housing 10 through the edge. That is, when the end face of the piston facing the first direction is a plane, the inner wall of the housing 10 can be set to a plane. When the end face of the piston facing the first direction is an arc surface, the inner wall of the housing 10 can be set to a corresponding concave surface. Compared with the diaphragm, the piston has a stronger compression capacity and is less likely to form gaps. The end face of the piston facing the second direction is connected to the linkage unit 20. The movement principle of the piston is the same as that of the diaphragm, and will not be repeated here.

[0273] Although the embodiments of the present invention have been described with reference to the accompanying drawings, those skilled in the art may make various modifications and variations without departing from the spirit and scope of the present invention. Such modifications and variations are all within the scope defined by the appended claims.

Claims

1. A fluid pumping unit for an oral cleaning appliance, characterized in that, Comprising: A housing (10) within which a fluid pump chamber (11) is formed, as well as a fluid input passage (12) and a fluid output passage (13) communicating with the fluid pump chamber (11); A displacement unit (40) movably disposed within the housing (10), the end face of the displacement unit (40) facing the first direction and the inner wall of the housing (10) enclosing to form the fluid pump chamber (11) with variable volume; A linkage unit (20) disposed within the housing (10) and drivingly connected to the end face of the displacement unit (40) facing the second direction, the linkage unit (20) being adapted to drive the displacement unit (40) to reciprocate in the first direction and the second direction, so as to cyclically increase and decrease the volume of the fluid pump chamber (11), such that the liquid in the fluid storage unit (50) is pumped into the fluid pump chamber (11) through the fluid input passage (12) and impact fluid is provided through the fluid output passage (13); A driving unit drivingly connected to the linkage unit (20), adapted to drive the linkage unit (20) to drive the displacement unit (40) to reciprocate; Among them, the displacement unit (40) has two limit positions during the reciprocating movement along the first direction and the second direction, and the distance between the two limit positions is in the range of 2.1 mm to 2.6 mm; the volume of the fluid pump chamber (11) is in the range of 120 mm 3 to 165 mm 3 range.

2. The fluid pumping unit according to claim 1, characterized in that, The linkage unit (20) includes: An eccentric wheel located within the housing (10) in the second direction opposite to the first direction of the displacement unit (40), the eccentric wheel having a rotation axis (21) deviating from its geometric center, the rotation axis (21) passing through the eccentric wheel and extending along the rotation axis of the eccentric wheel, the rotation axis being parallel and non-coincident with the central axis of the eccentric wheel; A connecting rod (30) located between the displacement unit (40) and the eccentric wheel, the first end of the connecting rod (30) being rotatably connected to the eccentric wheel, such that when the eccentric wheel rotates, it drives the connecting rod (30) to reciprocate in a direction perpendicular to the rotation axis (21); The second end of the connecting rod (30) extends towards the displacement unit (40) and is connected to the end face of the displacement unit (40) facing the second direction. During the reciprocating movement of the connecting rod (30), it drives the displacement unit (40) to cyclically increase and decrease the volume of the fluid pump chamber (11) with the same stroke as the connecting rod (30), such that the water in the fluid storage unit (50) is pumped into the fluid pump chamber (11) through the fluid input passage (12) and impact fluid is provided through the fluid output passage (13); wherein, the second end of the connecting rod (30) has two extreme positions of approaching or departing from the rotation axis (21) during the reciprocating movement, and the distance between the two extreme positions is in the range of 2.1 mm to 2.6 mm.

3. The fluid pumping unit according to claim 2, characterized in that, The driving unit (60) is a brushless motor, the rotation axis (21) is the output shaft of the brushless motor, and the rotational speed of the brushless motor is in the range of 3500 mrp to 4500 mrp.

4. The fluid pumping unit according to claim 2, wherein, The first end of the connecting rod (30) coincides with the geometric center of the eccentric wheel relative to the rotation center of the eccentric wheel, and the eccentricity of the eccentric wheel is in the range of 1.05 mm to 1.3 mm.

5. The fluid pumping unit according to claim 2, wherein, A balance weight (23) is connected to the eccentric wheel, and the balance weight (23) is adapted to increase the weight at the rotation axis (21) of the eccentric wheel to balance the torque during the rotation of the eccentric wheel.

6. The fluid pumping unit according to claim 1, characterized in that, The driving unit (60) is a linear motor, the linkage unit (20) is the output shaft of the linear motor, and the stroke of the output shaft is in the range of 2.1 mm to 2.6 mm.

7. The fluid pumping unit according to any one of claims 1 to 6, characterized in that, The volume of the fluid pump chamber (11) is in the range of 120 mm 3 to 130 mm 3 , and the distance between the two extreme positions of the displacement unit (40) during reciprocating movement is 2.2 mm.

8. The fluid pumping unit according to any one of claims 1 to 6, characterized in that, The volume of the fluid pump chamber (11) is within the range of 155 mm 3 to 165 mm 3 , and the distance between the two extreme positions of the displacement unit (40) during reciprocating movement is 2.4 mm.

9. The fluid pumping unit according to any one of claims 1 to 6, characterized in that, The inner diameter of the fluid input channel (12) is in the range of 2.0 mm to 3.0 mm.

10. The fluid pumping unit according to claim 9, characterized in that, The inner diameter of the fluid input channel (12) is in the range of 2.5 mm to 3.0 mm.

11. The fluid pumping unit according to any one of claims 1 to 6, characterized in that, The ratio of the calculated flow rate per unit time of the fluid pump chamber (11) to the actual flow rate per unit time of the fluid output channel (13) satisfies the following relationship: K = Q 流体泵腔 / Q 流体输出通道 ; Wherein, K is the ratio of the calculated flow rate per unit time of the fluid pumping unit to the actual flow rate per unit time of the fluid output channel (13); K is in the range of 2.93 ≤ K ≤ 3.75, and Q 流体泵腔 is the calculated flow rate per unit time of the fluid pump chamber (11), and Q 流体输出通道 is the actual flow rate per unit time of the fluid output channel (13).

12. The fluid pumping unit according to claim 11, wherein, The calculated flow rate per unit time of the fluid pump chamber (11) is calculated by the following formula: Q 流体泵腔 = nv; Wherein, n is the rotational speed of the eccentric wheel per unit time, and v is the volume of the fluid pump chamber (11).

13. The fluid pumping unit according to claim 1, characterized in that, The displacement unit (40) is a diaphragm or a piston.

14. An oral cleaning appliance, characterized in that, Comprising the fluid pumping unit according to any one of claims 1 to 13, further comprising: A holding housing (70), a spray head (80) is connected to an end of the holding housing (70), the fluid pumping unit is disposed in the holding housing (70), and the spray head (80) is in communication with the fluid output channel (13) of the fluid pumping unit; A fluid storage unit (50), disposed in the holding housing (70), and a water outlet of the fluid storage unit (50) is in communication with the fluid input channel (12) of the fluid pumping unit; A driving mechanism, disposed in the holding housing (70), and the driving mechanism is adapted to drive the eccentric wheel of the fluid pumping unit to rotate.

15. The oral cleaning appliance according to claim 14, wherein, The diameter of the liquid outlet hole of the spray head (80) is in the range of 0.6 mm to 0.65 mm.

16. The oral cleaning appliance according to claim 14, wherein, The volume of the fluid storage unit (50) is in the range of 50 ml to 200 ml.

17. The oral cleaning appliance according to claim 16, wherein, The volume of the fluid storage unit (50) is in the range of 50 ml to 90 ml.

18. The oral cleaning appliance according to claim 14, characterized in that, The fluid storage unit (50) is disposed below the fluid pumping unit and at the bottom of the holding housing (70), and a liquid injection port (51) communicating with the fluid storage unit (50) is provided on the lower side of the holding housing (70).

19. The oral cleaning appliance according to any one of claims 14 to 18, characterized in that, The oral cleaning appliance is a flushing integrated oral cleaning appliance, and a brush head is further provided at an end of the holding housing (70).

20. An oral cleaning appliance, characterized in that, Comprising: A holding housing (70), a spray head (80) and a brush head (90) are connected to an end of the holding housing (70); A fluid storage unit (50), disposed in the holding housing (70); A fluid pumping unit, disposed in the holding housing (70), comprising: A housing (10), a fluid pump chamber (11) is formed in the housing (10), and a fluid input channel (12) and a fluid output channel (13) communicating with the fluid pump chamber (11), the spray head (80) is in communication with the fluid output channel (13), and a water outlet of the fluid storage unit (50) is in communication with the fluid input channel (12); A displacement unit (40) is movably arranged in the housing (10). An end face of the displacement unit (40) facing the first direction and the inner wall of the housing (10) enclose to form the fluid pump chamber (11) with a variable volume. A linkage unit (20) is arranged in the housing (10) and is in driving connection with an end face of the displacement unit (40) facing the second direction. The linkage unit (20) is adapted to drive the displacement unit (40) to reciprocate along the first direction and the second direction, so as to cyclically increase and decrease the volume of the fluid pump chamber (11), so that the liquid in the fluid storage unit (50) is pumped into the fluid pump chamber (11) through the fluid input channel (12) and impact fluid is provided through the fluid output channel (13). A driving unit includes a first driving member (73) and a second driving member (60) arranged in the holding housing (70). The first driving member (73) is adapted to drive the brush head (90) to swing left and right to clean teeth. The second driving member is in driving connection with the linkage unit (20) and is adapted to drive the linkage unit (20) to drive the displacement unit (40) to reciprocate. Wherein, when the displacement unit (40) reciprocates along the first direction and the second direction, it has two limit positions, and the distance between the two limit positions is in the range of 2.1 mm to 2.6 mm. The volume of the fluid pump chamber (11) is in the range of 120 mm 3 to 165 mm 3 .

21. The oral cleaning appliance according to claim 20, wherein, A flushing handle (71) is connected to the top of the holding housing (70). The brush head (90) is installed at the end of the flushing handle (71). A fluid channel (711) is provided in the flushing handle (71). The nozzle (80) is installed at the end of the flushing handle (71) and is communicated with the fluid output channel (13) through the fluid channel (711). The first driving member (73) has a power output shaft (72) extending out of the holding housing (70). The flushing handle (71) is connected to the power output shaft (72) and performs a cleaning action under the control of the power output shaft (72).

22. The oral cleaning appliance according to claim 21, characterized in that, The power output shaft (72) is a columnar body penetrating through the upper and lower ends of the first driving member (73), and has an axial channel (721). The axial channel (721) has an outlet (722) communicated with the fluid channel (711) and an inlet (723) communicated with the fluid output channel (13).

23. The oral cleaning appliance according to claim 22, wherein, A connecting member (74) is provided between the inlet (723) and the fluid output channel (13). The connecting member (74) has a communication cavity (741), a first end (742) facing the fluid output channel (13), and a second end (743) facing the inlet (723). The fluid output channel (13) extends into the first end (742) of the connecting member (74), and the inlet (723) extends into the second end (743) of the connecting member (74).

24. The oral cleaning appliance according to claim 21, wherein, The end of the flushing handle (71) has a mounting groove (75), the mounting groove (75) has a boss (751), and the liquid outlet of the fluid channel is on the boss (751). The nozzle (80) is mounted on the boss (751); the brush head (90) includes a contact element carrier (901) mounted in the mounting groove (75), and a plurality of contact element clusters (902) spaced apart on the contact element carrier (901). There is a channel (903) on the contact element carrier (901) corresponding to the shape of the nozzle (80). Alternatively, the nozzle (80) and the brush head (90) are integrally formed and mounted on the mounting groove (75).

25. The oral cleaning appliance according to claim 20, characterized in that, The linkage unit (20) includes: An eccentric wheel, located in the second direction opposite to the first direction of the displacement unit (40) within the housing (10). The eccentric wheel has a rotation axis (21) deviating from its geometric center. The rotation axis (21) penetrates the eccentric wheel and extends along the rotation axis of the eccentric wheel. The rotation axis is parallel to and does not coincide with the central axis of the eccentric wheel; A connecting rod (30), located between the displacement unit (40) and the eccentric wheel. The first end of the connecting rod (30) is rotatably connected to the eccentric wheel, so that when the eccentric wheel rotates, it drives the connecting rod (30) to reciprocate in a direction perpendicular to the rotation axis (21); The second end of the connecting rod (30) extends towards the displacement unit (40) and is connected to the end face of the displacement unit (40) facing the second direction. During the reciprocating movement of the connecting rod (30), it drives the displacement unit (40) to cyclically increase and decrease the volume in the fluid pump chamber (11) with the same stroke as the connecting rod (30), so that the water in the fluid storage unit (50) is pumped into the fluid pump chamber (11) through the fluid input channel (12) and provides impact fluid through the fluid output channel (13); wherein, the second end of the connecting rod (30) has two extreme positions of approaching or departing from the rotation axis (21) during the reciprocating movement, and the distance between the two extreme positions is in the range of 2.1 mm to 2.6 mm.

26. The oral cleaning appliance according to claim 25, characterized in that, The second driving member (60) is a brushless motor disposed in the holding housing (70), the rotation axis (21) is the output shaft of the brushless motor, and the rotational speed of the brushless motor is in the range of 3500 mrp to 4500 mrp.

27. The oral cleaning appliance according to claim 25, wherein, The rotation center of the first end of the connecting rod (30) relative to the eccentric wheel coincides with the geometric center of the eccentric wheel, and the eccentricity of the eccentric wheel is in the range of 1.05 mm to 1.3 mm.

28. The oral cleaning appliance according to claim 27, wherein, A balance weight (23) is connected to the eccentric wheel. The balance weight (23) is adapted to increase the weight at the rotation axis (21) of the eccentric wheel to balance the torque during the rotation of the eccentric wheel.

29. The oral cleaning appliance according to claim 20, wherein, The second driving member (60) is a linear motor disposed within the holding housing (70), the linkage unit (20) is the output shaft of the linear motor, and the stroke of the output shaft is in the range of 2.1 mm to 2.6 mm.

30. The oral cleaning appliance according to any one of claims 20 to 29, characterized in that, During the reciprocating movement of the displacement unit (40) along the first direction and the second direction, there are two limit positions, and the distance between the two limit positions is in the range of 2.2 mm to 2.4 mm.

31. The oral cleaning appliance according to claim 30, wherein, The volume of the fluid pump chamber (11) is within the range of 120 mm 3 to 130 mm 3 and the distance between the two extreme positions of the displacement unit (40) during reciprocating movement is 2.2 mm.

32. The oral cleaning appliance according to claim 30, wherein, The volume of the fluid pump chamber (11) is within the range of 155 mm 3 to 165 mm 3 and the distance between the two extreme positions of the displacement unit (40) during reciprocating movement is 2.4 mm.

33. The oral cleaning appliance according to any one of claims 20 to 10, characterized in that, The inner diameter of the fluid input channel (12) is in the range of 2.0 mm to 3.0 mm.

34. The oral cleaning appliance according to claim 33, wherein, The inner diameter of the fluid input channel (12) is in the range of 2.5 mm to 3.0 mm.

35. The oral cleaning appliance according to any one of claims 20 to 29, characterized in that, The ratio of the calculated flow rate per unit time of the fluid pump chamber (11) to the actual flow rate per unit time of the fluid output channel (13) satisfies the following relationship: K = Q 流体泵腔 / Q 流体输出通道 ; where K is the ratio of the calculated flow rate per unit time of the fluid pump chamber to the actual flow rate per unit time of the fluid output passage (13); K is in the range of 2.93 ≤ K ≤ 3.75, and Q 流体泵腔 is the calculated flow rate per unit time of the fluid pump chamber (11), and Q 流体输出通道 is the actual flow rate per unit time of the fluid output passage (13).

36. The oral cleaning appliance according to claim 35, wherein, The flow rate per unit time of the fluid pump chamber (11) is calculated by the following formula: Q 流体泵腔 = nv; where n is the rotational speed of the eccentric wheel per unit time, and v is the volume of the fluid pump chamber (11).

37. The oral cleaning appliance according to claim 33, wherein, The diameter of the fluid output holes of the nozzle (80) is in the range of 0.6 mm to 0.65 mm.

38. The oral cleaning appliance according to claim 20, wherein, The volume of the fluid storage unit (50) is in the range of 50 ml to 200 ml.

39. The oral cleaning appliance according to claim 36, wherein, The volume of the fluid storage unit (50) is in the range of 50 ml to 90 ml.

40. The oral cleaning appliance according to claim 20, wherein, The displacement unit (40) is a diaphragm or a piston.

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