Fluid pumping unit and oral cleaning device

Abstract

The present invention provides a fluid pumping unit and an oral cleaning device, comprising a shell, a displacement unit, and an interlocking unit. The displacement unit is movably mounted on the shell, and an end face of the displacement unit facing a first direction and an inner wall of the shell surround each other to form a variable fluid pump chamber having a sealed volume. The interlocking unit is mounted on the shell and connected to an end face of the displacement unit facing a second direction, and is configured to drive the displacement unit to reciprocate along the first direction and the second direction, thereby cyclically increasing and decreasing the volume of the fluid pump chamber, pumping liquid in a container into the fluid pump chamber through a fluid input channel and providing impulse fluid through a fluid output channel, wherein the displacement unit has two limit positions during reciprocating movement in the first direction and the second direction, the distance between the two limit positions being within a range of 2.1 mm to 2.6 mm, and the volume of the pump liquid cavity is 120 mm. 3 ~165mm 3 is within the range.

Description

[Technical Field]

[0001] This application claims priority to a Chinese patent application filed on December 29, 2023, entitled "Fluid Pumping Unit and Oral Cleansing Device," application number 202311867128.3, and a Chinese patent application filed on December 29, 2023, entitled "Oral Cleansing Device," application number 202311869907.7, the entire contents of which are incorporated herein by reference.

[0002] The present invention relates to the technical field of oral cleaning devices, and in particular to a fluid pumping unit and an oral cleaning device. [Background technology]

[0003] A water flosser is a typical oral care device that generally comprises a spray head and a handle. The handle is provided with a pump body connected to the spray head and a water tank connected to the pump body. In use, the pump body pumps water from the water tank, and the pump body and the variable diameter pipeline jointly pressurize the water flow, which is then discharged from the spray head. The pressurized water flow can be used to clean the user's teeth.

[0004] To ensure cleaning power, prior art water flossers generally use conventional pump bodies that are large in size and consume a lot of water. To meet the water consumption requirements of the pump body, the volume of the water tank must be increased, but the overall size of the handle is too large, degrading the user experience. The usual improvement method is to keep the volume of the pump body constant and reduce the volume of the water tank, which reduces the size of the handle to a certain extent, but this affects the amount of water output from the spray head, reducing cleaning power and affecting the cleaning effect. Therefore, prior art water flossers are unable to resolve the contradiction between product size and cleaning power. Summary of the Invention [Problem to be solved by the invention]

[0005] SUMMARY OF THE INVENTION In view of the above, the present invention provides a fluid pumping unit and an oral cleaning implement that solves the problem of prior art water flossers, which have a trade-off between product size and cleaning power. [Means for solving the problem]

[0006] According to a first aspect, the present invention provides a fluid pumping device comprising: a shell having a fluid pumping chamber formed therein, and a fluid input channel and a fluid output channel communicating with the fluid pumping chamber; a displacement unit movably provided on the shell, the end face facing a first direction being enclosed together with an inner wall of the shell to form the fluid pumping chamber having a variable sealed volume; a linkage unit provided on the shell and transmission-connected to an end face facing a second direction of the displacement unit, the linkage unit driving the displacement unit to reciprocate along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pumping chamber, pumping liquid in a fluid storage unit into the fluid pumping chamber via the fluid input channel and providing an impact fluid through the fluid output channel; and a drive unit transmission-connected to the linkage unit to drive the linkage unit to reciprocate the displacement unit, the displacement unit having two limit positions during reciprocal movement in the first direction and the second direction, the distance between the two limit positions being within a range of 2.1 mm to 2.6 mm, and the volume of the fluid pumping chamber being 120 mm. 3 ~165mm 3 To provide a fluid pumping unit for an oral cleaning device within the range of

[0007] According to a second aspect, the present invention provides an oral cleaning device comprising a gripping case, a fluid storage unit, and a drive mechanism, wherein a spray head is connected to an end of the gripping case, the fluid pumping unit is disposed within the gripping case, the spray head is connected to a fluid output channel of the fluid pumping unit, the fluid storage unit is disposed within the gripping case, the outlet of the fluid storage unit is connected to a fluid input channel of the fluid pumping unit, and the drive mechanism is disposed within the gripping case and configured to drive the eccentric wheel of the fluid pumping unit in rotation.

[0008] According to a third aspect, the present invention further provides an oral cleaning device comprising a grip shell, a fluid storage unit, a fluid pumping unit, and a drive mechanism, wherein a spray head and a brush head are connected to an end of the grip case, the fluid storage unit is disposed in the grip case, and the fluid pumping unit is disposed in the grip case, the fluid pumping unit comprising a shell having a fluid pump chamber formed therein, a fluid input channel and a fluid output channel communicating with the fluid pump chamber, the spray head being communicated with the fluid output channel and the water outlet of the fluid storage unit being communicated with the fluid input channel, a displacement unit movably provided in the shell, the end face facing a first direction surrounding the inner wall of the shell to form the fluid pump chamber of a variable sealed volume, and an interlocking unit provided in the shell and communicatively connected to the end face facing a second direction of the displacement unit, the interlocking unit being capable of transmitting and receiving force in the first direction and the second direction. a linkage unit configured to drive the brush head to reciprocate along the fluid pump chamber to cyclically increase and decrease a volume of the fluid pump chamber, pump liquid in the fluid storage unit into the fluid pump chamber through the fluid input channel, and provide impact fluid through the fluid output channel; and a drive unit including a first drive member and a second drive member disposed in the grip case, wherein the first drive member is configured to drive the brush head to clean teeth, and the second drive member is transmission-coupled to the linkage unit and configured to drive the linkage unit to reciprocate the displacement unit, wherein the displacement unit has two limit positions during reciprocating movements in the first direction and the second direction, a distance between the two limit positions is within a range of 2.1 mm to 2.6 mm, and a volume of the fluid pump chamber is 120 mm. 3 ~165mm 3 is within the range. [Effects of the Invention]

[0009] The principle of the fluid pumping unit of the present invention is that the displacement unit is driven by the interlocking unit to move back and forth, thereby cyclically increasing and decreasing the volume of the fluid pump chamber, thereby cyclically increasing and decreasing the pressure in the fluid pump chamber. When the volume of the fluid pump chamber decreases, water in the fluid storage unit enters the fluid pump chamber due to the negative pressure. When the volume of the fluid pump chamber increases, the water in the fluid pump chamber enters the fluid output channel, forming an impinging water flow, which then forms a pulse jet. The pulse jet is a discontinuous water flow that can generate huge transient energy through the water hammer effect, thereby reducing water consumption and increasing the impact force of the water flow to ensure a cleaning effect. The distance between the two limit positions of the displacement unit is within the range of 2.1mm to 2.6mm, and the volume of the fluid pump chamber is 120mm. 3 ~165mm 3 By keeping the range within this range, not only can the impact force of the water flow be ensured, but also the size of the fluid pumping unit can be reasonably reduced based on this. In this way, the cleaning effect can be ensured with a smaller water flow rate, and the size of the fluid pumping unit and the fluid storage unit can be reduced, which can significantly reduce the size of the handle.

[0010] The spray head and brush head on the handle case can function as both a water flosser and an electric toothbrush, allowing users to use the two cleaning methods independently or simultaneously. The fluid pumping unit operates by driving the displacement unit to move back and forth via the interlocking unit, cyclically increasing and decreasing the volume of the fluid pump chamber, thereby cyclically increasing and decreasing the pressure within the fluid pump chamber. When the pressure in the fluid pump chamber decreases, the liquid in the fluid storage unit flows into the fluid pump chamber due to the negative pressure. When the pressure in the fluid pump chamber increases, the liquid in the fluid pump chamber flows into the fluid output channel, forming an impulse fluid, which then forms a pulse jet. The pulse jet is a discontinuous fluid, and can generate large transient energy through the water hammer effect, reducing fluid consumption while increasing the fluid impact force and ensuring effective cleaning. The distance between the two limit positions of the displacement unit is within the range of 2.1mm to 2.6mm, and the volume of the fluid pump chamber is 120mm. 3 ~165mm 3 By keeping the water flow impact force within this range, not only can the water flow impact force be ensured, but the size of the fluid pumping unit can also be reasonably reduced based on this, and the size of the handle case can also be reduced. This method ensures that the oral cleaning device simultaneously combines the cleaning functions of an electric toothbrush and a water flosser, and while ensuring the fluid impact force, it not only reduces the size of the fluid pumping unit but also saves liquid. Furthermore, the volume of the fluid storage unit can be further reduced, which reduces the size of the handle case and the weight of the integrated oral cleaning water flosser, providing a better user experience. [Brief explanation of the drawings]

[0011] In order to describe in more detail certain embodiments of the present invention or technical solutions of the prior art, the following will briefly describe the drawings necessary for describing certain embodiments or prior art. Of course, the drawings in the following description are only some embodiments of the present invention, and those skilled in the art can obtain other drawings based on these drawings without performing creative work. [Figure 1A] 1 is a structural schematic diagram showing an oral care device according to an embodiment of the present invention; [Figure 1B] 1 is a structural schematic diagram showing another oral care device according to an embodiment of the present invention. [Figure 2] 1 is a structural schematic diagram of a fluid pumping unit according to an embodiment of the present invention; [Figure 3] FIG. 3 is a schematic cross-sectional view of the fluid pumping unit in FIG. 2. [Figure 4] FIG. 4 is an enlarged schematic view showing a portion A in FIG. 3. [Figure 5] 4 is a structural schematic diagram showing a fitting connection between the eccentric wheel and the balance weight in FIG. 3.

[0023] FIG. [Figure 6] FIG. 6 is a structural schematic diagram of the elevation angle showing the fitting connection between the eccentric wheel and the balance weight in FIG. 5. [Figure 7] FIG. 6 is a structural schematic diagram showing the fitting connection between the eccentric wheel and the balance weight in FIG. 5 as viewed from above. [Figure 8] 4 is a diagram illustrating experimental parameters of a fluid pumping unit according to an embodiment of the present invention. [Figure 9] 10 is a schematic diagram showing the relationship between impact force and two limit position distances of a link. FIG. [Figure 10] FIG. 10 is a schematic diagram showing the relationship between the water extraction time and two limit position distances of the link. [Figure 11] FIG. 1 is a schematic diagram showing the relationship between impact force and the inner diameter of a fluid input channel. [Figure 12] FIG. 10 is a schematic diagram showing the relationship between the flow rate per unit time of a fluid pump chamber and the inner diameter of a fluid input channel. [Figure 13] 1 is a structural schematic diagram showing a flushing handle according to an embodiment of the present invention; [Figure 14] 3 is a structural schematic diagram showing the mounting position of the power output shaft and the fluid pumping unit according to the embodiment of the present invention; FIG. [Figure 15] 1 is a structural schematic diagram showing a connecting member according to an embodiment of the present invention; [Figure 16] 1 is a schematic diagram of the explosion structure of a flushing handle according to an embodiment of the present invention; [Figure 17] FIG. 2 is a schematic diagram of an explosion structure showing a power output member, a front damping pad, and a rear damping pad. DETAILED DESCRIPTION OF THE INVENTION

[0012] Currently, oral irrigators can combine the functions of a water flosser and an electric toothbrush, cleaning teeth and between teeth at the same time. Oral irrigators include a brush head and a spray head. When in use, the brush head is used to scrape off bacteria and food residue adhering to the surface of the teeth, and the spray head's rinsing function is used to remove bacteria and food residue adhering to between the teeth. By combining the two, bacteria and food residue on the surface of the teeth and between the teeth can be effectively removed, preventing oral problems and improving oral health.

[0013] To facilitate the rinsing function, conventional oral cleaning devices typically use two independent motors to drive the brush head and spray head, increasing the device's weight to a certain extent. The tooth-cleaning function, in particular, requires a pump body and a water tank connected to the pump body. During use, the pump body pumps water from the water tank, pressurizing it through the pump body and a variable-diameter pipeline, which then discharges the water from the spray head, allowing the user to clean their teeth. To ensure cleaning power, conventional pump bodies are typically large and consume a lot of water. To meet the water demands of the pump body, the water tank's volume must be increased, further increasing the weight and size of the oral cleaning device, making it difficult for the user to hold and degrading the user's experience. A typical improvement approach is to keep the pump body volume constant and reduce the volume of the water tank, thereby reducing the handle size to a certain extent, but this affects the amount of water discharged from the spray head, reducing cleaning power and negatively impacting cleaning results. Therefore, the conventional oral cleaning devices are unable to resolve the trade-off between product size and cleaning power.

[0014] Therefore, the present application provides a fluid pumping unit and oral cleaning implement that solves the problem of prior art water flossers, where there is a trade-off between product size and cleaning power.

[0015] In the following, the technical means in the embodiments of the present invention will be clearly and completely described with reference to the drawings in the embodiments of the present invention, in order to make the objectives, technical means and advantages of the embodiments of the present invention clearer. Of course, the embodiments described here are only a part, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative efforts are all included in the protection scope of the present invention.

[0016] As shown in Figures 1A and 2 to 4, the fluid pumping unit of the oral cleaning device of the present application comprises a shell 10, a displacement unit 40, a linkage unit 20, and a drive unit, which is a second drive member 60.

[0017] The shell 10 is formed with a fluid pump chamber 11 and a fluid input channel 12 and a fluid output channel 13 communicating with the fluid pump chamber 11. Because the fluid pump chamber 11 mainly utilizes changes in internal pressure to realize liquid inflow and outflow, check valves can be disposed in the fluid input channel 12 and the fluid output channel 13, respectively. Here, the check valve in the fluid input channel 12 allows liquid to flow from the fluid storage unit to the fluid pump chamber 11, and the check 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 may be fresh water, mouthwash, oral care liquid, etc., and the fluid storage unit 50 is for containing the liquid. For ease of uniformity, the following description will be given taking water as an example.

[0018] Furthermore, the fluid input channel 12 is connected to the fluid storage unit 50, and the fluid output channel 13 is connected to the spray head 80. When the pressure in the fluid pump chamber 11 increases, the water in the fluid pump chamber 11 flows out of the spray head 80 through the fluid output channel 13, and the check valve in 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 flows into the fluid pump chamber 11 through the fluid input channel 12, and the check valve in the fluid output channel 13 prevents the water in the fluid output channel 13 from flowing back into the fluid pump chamber 11.

[0019] The displacement unit 40 is movably mounted on the shell 10, and the end face of the displacement unit 40 facing in the first direction, together with the inner wall of the shell 10, forms a sealed, variable-volume fluid pump chamber 11. In this embodiment, the edge of the displacement unit 40 may be tightly attached to the inner wall of the shell 10. Therefore, a sealed chamber is formed by the inner wall of the shell 10 positioned in the first direction and the diaphragm sheet, and this chamber is the fluid pump chamber 11. The movably positioned displacement unit 40 allows the volume of the fluid pump chamber 11 to be variable, and the fluid input channel 12 and the fluid output channel 13 are also positioned in the first direction and communicate with the fluid pump chamber 11. When the volume of the fluid pump chamber 11 changes due to the placement of the check valve, the pressure in the fluid pump chamber 11 also increases or decreases. Therefore, 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 to the fluid output channel 13.

[0020] 3, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, with the displacement unit 40 as the boundary, and the interlocking unit 20 that drives the displacement unit 40 to move is located in a second direction opposite to the first direction. This configuration facilitates wet / dry separation, prevents liquid from entering the movement space of the interlocking unit 20, and avoids affecting the interlocking unit 20 and other electrical components.

[0021] The linkage unit 20 is provided on the shell 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction, and the linkage unit 20 drives the displacement unit 40 to move back and forth along the first direction and the second direction, thereby cyclically increasing and decreasing the volume of the fluid pump chamber 11, pumping the liquid in 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.

[0022] As shown in FIG. 3 , the displacement unit 40 reciprocates along the first and second directions. The displacement unit 40 enters the fluid pump chamber 11, and the displacement unit 40 cyclically increases and decreases the volume of the fluid pump chamber 11 to pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 and provide impact fluid through the fluid output channel 13. The second driving member 60 is transmission-coupled to the linkage unit 20 and configured to drive the linkage unit 20 to reciprocate the displacement unit 40. Here, the displacement unit 40 has two limit positions during reciprocating movement in the first and second directions, and the distance between the two limit positions is within a range of 2.1 mm to 2.6 mm, and the volume of the fluid pump chamber 11 is 120 mm. 3 ~165mm 3 is within the range.

[0023] Specifically, the displacement unit 40, the sidewall of the fluid pump chamber 11, the check valve of the fluid input channel 12, and the check valve of the fluid output channel 13 together form a sealed space. The movement of the displacement unit 40 changes the volume of the sealed space, and the pressure in the fluid pump chamber 11 increases or decreases accordingly. When the pressure in the fluid pump chamber 11 decreases, negative pressure acts to pump liquid from the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12. When the pressure in the fluid pump chamber 11 increases, liquid is expelled from the fluid pump chamber 11 through the fluid output channel 13, forming an impinging water flow. Because the fluid pump chamber 11 must suck in and then expel liquid again, 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 pulsed water flow can generate huge transient energy through the water hammer effect, thereby increasing the impact force of the impinging water flow and further improving the cleaning effect. Pulsed water flow also reduces water consumption compared to continuous water flow, reducing the volume of the fluid storage unit and reducing the size of the aircraft.

[0024] Based on this, the distance between the two limit positions of the displacement unit 40 can be set within a range of 2.1 mm to 2.6 mm, which is sufficient to meet the pressure change requirements in the fluid pump chamber 11. This reduces the space required to support the movement of the interlocking unit 20 within the shell 10, further reducing the design size of the shell 10 and the overall size of the aircraft. According to the technical solution of this embodiment, the interlocking unit 20 drives the displacement unit 40 to move back and forth, allowing the fluid output channel 13 to form a pulse jet, ensuring impact force while saving fluid consumption. This allows the use of a smaller fluid storage unit to meet fluid consumption needs. At the same time, the distance between the two limit positions of the displacement unit 40 is set within a range of 2.1 mm to 2.6 mm, which reduces the space required to support the movement of the interlocking unit 20 and the displacement unit 20 within the shell 10 and thus reduces the size of the shell 10.

[0025] In one embodiment of this example, the linkage unit 20 includes an eccentric and a link 30 .

[0026] The eccentric is located in the shell 10 in a second direction opposite to the first direction of the displacement unit 40, and has a rotation axis 21 offset from its geometric center, which passes through the eccentric and extends along the rotation axis of the eccentric, which is parallel to but does not overlap with the central axis of the eccentric. A link 30 is located between the displacement unit 40 and the eccentric, and a first end of the link 30 is rotatably connected to the eccentric, driving the link 30 to move back and forth along a direction perpendicular to the rotation axis 21 when the eccentric rotates. The second end of the link 30 extends toward the displacement unit 40 and is connected to an end face of the displacement unit 40 facing the second direction. During the reciprocating movement of the link 30, the displacement unit 40 is driven to cyclically increase or decrease the volume in the fluid pump chamber 11 with the same stroke as the link 30, thereby pumping water in the fluid storage unit 50 into the fluid pump chamber 11 via the fluid input channel 12 and providing impact fluid through the fluid output channel 13. Here, the second end of the link 30 has two limit positions during the reciprocating movement, where it approaches the pivot shaft 21 and moves away from the pivot shaft 21, and the distance between the two limit positions is within a range of 2.1 mm to 2.6 mm.

[0027] As shown by the dashed arrow in Figure 3, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, with the displacement unit 40 as the boundary, and the link 30 and eccentric wheel that drive and move the displacement unit 40 are located in a second direction opposite to the first direction. This configuration facilitates the separation of dry and wet fluids, prevents liquid from entering the movement space of the link 30 and eccentric wheel, and avoids any impact on the interlocking unit 20 and other electrical components.

[0028] The link 30 is provided on the shell 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction, and the link 30 drives the displacement unit 40 to move back and forth along the first direction and the second direction, thereby cyclically increasing and decreasing the volume of the fluid pump chamber 11, pumping the liquid in 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.

[0029] The eccentric is positioned within the shell 10 in a second direction opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 that is offset from its geometric center. The eccentric is configured to rotate around the rotation axis 21, which passes through the eccentric and extends along the rotation axis of the eccentric, which is parallel to but does not overlap with the central axis of the eccentric. The geometric center of the eccentric is the central position of the eccentric's geometric shape. Therefore, when the eccentric rotates around the rotation axis 21, it performs an eccentric rotational motion.

[0030] The link 30 is located between the displacement unit 40 and the eccentric wheel, and a first end of the link 30 is rotatably connected to the eccentric wheel, and when the eccentric wheel rotates, the link 30 is driven to move back and forth along a direction perpendicular to the rotation axis 21, and a second end of the link 30 extends in a direction away from the rotation axis 21, and the displacement unit 40 moves back and forth along the first and second directions as shown in FIG. 3 . The first end of the link 30 can be used as a power input end, and the first end of the link 30 can rotate around the rotation center by driving the eccentric wheel, and the second end opposite to the first end can be used as a power output end, and the second end of the link 30 can move back and forth along the direction perpendicular to the rotation axis 21.

[0031] The displacement unit 40 is connected to the second end of the link 30 and projects into the fluid pump chamber 11. The plane of the displacement unit 40 acting on the fluid pump chamber 11 is arranged parallel to the pivot shaft 21. During the reciprocating movement of the link 30, the displacement unit 40 cyclically increases and decreases the volume within the fluid pump chamber 11, thereby pumping water from the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 in the oral cleaning device and providing an impinging water flow through the fluid output channel 13. Here, the second end of the link 30 has a limit position close to the pivot shaft 21 and a limit position far from the pivot shaft 21 during the reciprocating movement, the distance between the two limit positions being within a range of 2.1 mm to 2.6 mm, and the volume of the fluid pump chamber 11 is 120 mm. 3 ~165mm 3 is within the range.

[0032] Based on this, the distance between the two limit positions of the link 30 can be set within a range of 2.1 mm to 2.6 mm, which is sufficient for the displacement unit 40 to meet the pressure change requirements in the fluid pump chamber 11. This reduces the space required to support the movement of the link 30 within the shell 10, further reducing the design size of the shell 10 and the overall size of the aircraft. According to the technical solution of this embodiment, the rotation of the eccentric wheel drives the displacement unit 40 to move back and forth via the second end of the link 30, allowing the fluid output channel 13 to form a pulse jet, ensuring impact force while saving fluid consumption. This allows the use of a smaller fluid storage unit to meet fluid consumption needs. At the same time, the distance between the two limit positions of the link 30 is set within a range of 2.1 mm to 2.6 mm, which reduces the space required to support the movement of the link 30 within the shell 10 and thus reduces the size of the shell 10. The second driving member 60 is a brushless motor provided inside the holding case 70, and the rotary shaft 21 is the output shaft of the brushless motor, whose rotation speed is in the range of 3500 mrp to 4500 mrp. The brushless motor has excellent torque characteristics and a wide speed adjustment range, eliminating the need for a separate gearbox, further simplifying the structure and reducing the size of the holding case 70.

[0033] 3, the dashed arrows in the figure indicate the effective movement directions of the link 30, i.e., the link 30 must reciprocate in the first and second directions, and the link 30 has two limit positions located in the first and second directions, respectively. When the link 30 moves to the limit position in the first direction, the diaphragm seat discharges the liquid from the fluid pump chamber 11. When the link 30 moves to the limit position in the second direction, the distance between the diaphragm seat and the opposite fluid pump chamber 11 is maximized, reducing the pressure in the fluid pump chamber 11 and causing liquid to flow from the fluid input channel 12 into the fluid pump chamber 11.

[0034] As shown in Figures 3 and 4, the edge of the displacement unit 40 is fixed to the side wall of the fluid pump chamber 11, and the displacement unit 40 and the second end of the link 30 can be connected by a screw. The displacement unit 40 can be injection molded integrally with the screw, which simplifies the structure and reduces the difficulty of assembly.

[0035] 3 and 4, the shell 10 has a cavity for accommodating the eccentric wheel, and the second driving member 60 is located at the bottom of the shell 10. The output shaft of the second driving member 60 extends into the cavity and couples with the eccentric wheel to form the rotating shaft 21, and the drive unit can drive the eccentric wheel to rotate via the rotating shaft 21. For example, an on-axis roller pattern can be provided on the rotating shaft 21, and the eccentric wheel can be press-fitted into the on-axis roller pattern. The on-axis roller pattern can increase the friction between the rotating shaft 21 and the eccentric wheel, ensuring that the rotating shaft 21 can drive the eccentric wheel to rotate smoothly. A shaft base is provided in the cavity, and the end of the output shaft of the second driving member 60 extends into the shaft base, improving the rotational stability of the output shaft. In addition to providing accommodation space for the above components, the cavity must also provide a certain amount of movement space for the rotation of the eccentric wheel and the reciprocating movement of the first end of link 30. By setting the distance between the two limit positions of link 30 to 2.1 mm to 2.6 mm, the size of the movement space within the cavity can be limited, thereby reducing the overall design size of shell 10.

[0036] The applicant has demonstrated through a large amount of experimental data that if the distance between the two limit positions of the link 30 is less than 2.1 mm, the pumping force will be weak, resulting in an insufficient pumped water flow rate and failing to meet the water flow impact force requirements, and if the distance between the two limit positions of the link 30 is more than 2.6 mm, the design size of the cavity will be too large to meet the requirement of reducing the overall design size of the shell 10. Therefore, the distance between the two limit positions of the link 30 is set to 2.1 mm to 2.6 mm, and may be, for example, 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm, or 2.6 mm.

[0037] In this embodiment, the first end of the link 30 overlaps with the geometric center of the eccentric wheel relative to the rotation center of the eccentric wheel, and the eccentric distance of the eccentric wheel is within the range of 1.05 mm to 1.3 mm. When the first end of the link 30 overlaps with the collective center of the eccentric wheel relative to the rotation center of the eccentric wheel, the movement stroke of the second end of the link is twice the eccentric distance of the eccentric wheel. If the eccentric distance of the eccentric wheel is set within the range of 1.05 mm to 1.3 mm, the distance between the two limit positions of the link 30 can be ensured to be within the range of 2.1 mm to 2.6 mm.

[0038] As shown in Figures 4 and 5, in this embodiment, the cross section of the eccentric perpendicular to the pivot axis 21 is circular. A trepanning member is provided at the first end of the link 30, with the axis of the trepanning member parallel to the pivot axis 21 and fitted over the outside of the eccentric. The eccentric has a shaft hole 201 that fits over the pivot axis 21. The eccentric is circular, and the trepanning member may also be circular. This reduces friction between the eccentric and the first end of the link 30 and ensures that the first end of the link 30 passes through the trepanning member and fits against the outer edge of the eccentric for reciprocating circular motion. The eccentric rotates 360° around the pivot axis 21, completing one full stroke of the link 30. It is more advantageous to control the distance between the two limit positions of the link 30 to be between 2.1 mm and 2.6 mm, ensuring that the movement of the displacement unit 40 provides a stable pressure difference.

[0039] In order to further reduce the frictional force between the eccentric and the trepanning, a bearing 22 fitted on the eccentric can be provided between the eccentric and the link 30, and the trepanning is fitted on the bearing 22, which can reduce the frictional force between the eccentric and the link 30, preventing the eccentric from driving the link to rotate coaxially, and ensuring that the link 30 can move back and forth cyclically in a direction perpendicular to the rotation axis 21.

[0040] Because the center of mass of the eccentric wheel is not located on the axis of the rotating shaft 21, an unbalanced centrifugal force is generated as the eccentric wheel rotates, and the unbalanced torque generated increases the load on the output shaft of the second driving member 60, increasing the frictional resistance of the shaft protrusion and the amount of heat generated.

[0041] 5, 6 and 7, in this embodiment, a balance weight 23 is connected to the eccentric wheel, and the balance weight 23 increases the weight of the eccentric wheel on the rotating shaft 21 in order to balance the torque during the rotation of the eccentric wheel. Specifically, the opposing ends of the balance weight 23 have different weights, with the heavier end being located at the top of the shaft hole 201 and extending to the end face where the shaft hole 201 penetrates the balance weight 23, and the lighter end being located at the top of the side facing the shaft hole 201. With this configuration, the mass on the rotating shaft 21 side can be increased, and further, since the weights of both opposing sides of the eccentric wheel centered on the rotating shaft 21 are the same or nearly the same, the centrifugal forces on both ends of the eccentric wheel are the same when the eccentric wheel rotates, solving the problem of imbalance in centrifugal forces on both ends of the eccentric wheel, balancing the torque of the output shaft of the second driving member 60, making the rotation of the output shaft of the second driving member 60 more stable, reducing the frictional resistance of the shaft protrusions, and reducing the amount of heat generated. In addition, by arranging the balance weight 23 above the eccentric wheel, motion interference between the balance weight 23 and the link 30 can be avoided, and interference in the transmission between the eccentric wheel and the link 30 can be avoided.

[0042] In a specific embodiment of this embodiment, the cross section of the balance weight 23 may be symmetrical, but as shown by the dashed lines in Figures 6 and 7, the balance weight 23 has an axis of symmetry. This configuration can avoid the introduction of new unbalance forces. Specifically, taking the direction shown in Figure 7 as an example, the balance weight 23 generally has two arcuate sides in the left-right direction, with the left arcuate side being shorter than the right arcuate side, and a hypotenuse in the up-down direction, with the rightward arc of the hypotenuse inclined outward. As a result, the size of the right side of the balance weight 23 is larger than the size of the left side, and when the density of the balance weight 23 is equalized, i.e., the weight of the right side of the balance weight 23 is greater than the weight of the left side, the centrifugal forces on both the left and right sides are balanced when the eccentric wheel rotates.

[0043] Of course, the structure of the balance weight 23 can also be adjusted accordingly, but it is only necessary to increase the weight in the axial hole 201 of the eccentric.

[0044] In this embodiment, the eccentric wheel and balance weight 23 are integrally molded, which facilitates productivity and reduces assembly errors. Although a fastening member or the like may be used, the balance weight 23 may be fixed to the eccentric wheel via a screw, for example, which makes it easier to adjust or replace the balance weight 23 thereafter.

[0045] In another embodiment of this embodiment, the second driving member 60 is a linear motor arranged in the gripping case 70, the interlocking 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, and the output shaft of the linear motor drives the displacement unit 40 to move back and forth, and applies a cyclically increasing and decreasing pressure to the fluid pump chamber 11.

[0046] In this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3 ~165mm 3The water output volume per unit time of the fluid output channel 13 is related to the volume of the fluid pump chamber 11. Specifically, the water output volume per unit time of the fluid output channel 13 increases as the volume of the fluid pump chamber 11 increases. If the pipe diameter of the fluid output channel 13 does not change, the impact force of the water flow increases as the water output volume per unit time increases. The applicant has found through a large amount of experimental data that when the distance between the two limit positions of the link 30 is 2.2 mm to 2.4 mm, the impact force of the water flow increases when the volume of the fluid pump chamber 11 is 120 mm. 3 ~165mm 3 It has been demonstrated that the pressure of the fluid output channel 13 not only meets the impact force requirement, but also meets the water saving requirement. 3 If the volume of the fluid pump chamber 11 is less than 165 mm, the water flow rate will be too small to meet the impact force requirement. 3 If it is larger than , the impact force requirement can be met, but the amount of water discharged per unit time is too large, which means that the water consumption in the fluid storage unit 50 is too fast to meet the requirement of the cleaning time, which affects the cleaning effect.

[0047] More preferably, in this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 , the distance between the two limit positions during the reciprocating movement of the link 30 is selected to be 2.2 mm.

[0048] For example, the volume of the fluid pump chamber 11 is 120 mm 3 , 121mm 3 , 122mm 3 , 123mm 3 ...or 130mm 33, when the second end of the link 30 moves to the limit position in the first direction, the diaphragm seat is completely and tightly pressed against the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged. If the limit position is greater than 2.2 mm, motion interference occurs between the diaphragm seat and the side wall of the fluid pump chamber 11 during the process of the second end of the link 30 moving to the limit position in the first direction.

[0049] More preferably, in this embodiment, the volume of the fluid pump chamber is 155 mm 3 ~165mm 3 If the distance between the two limit positions during the reciprocating movement of the link is within the range of 2.4 mm, the distance between the two limit positions during the reciprocating movement of the link is selected to be 2.4 mm.

[0050] For example, the volume of the fluid pump chamber 11 is 155 mm 3 , 156mm 3 , 157mm 3 , 158mm 3 ...or 165mm 3 3, when the second end of the link 30 moves to the limit position in the first direction, the diaphragm seat is brought into complete contact with the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged. If the limit position is less than 2.4 mm, a gap will exist between the diaphragm seat and the side wall of the fluid pump chamber 11 when the second end of the link 30 moves to the limit position in the first direction, reducing the operating efficiency of the fluid pump chamber 11.

[0051] In this embodiment, by optimizing each parameter of the fluid pumping unit, the fluid pumping unit can be made more water-efficient while maintaining cleaning power, thereby making it possible to reduce the size of the fluid storage unit in the oral cleaning device, thereby resolving the contradiction between product size and cleaning power that exists in water flossers in conventional technology.

[0052] The principles of movement of each component of the fluid pumping unit in this embodiment have been explained above. Below, the basis for the values ​​of each parameter of the fluid pumping unit in this embodiment will be explained in detail.

[0053] 1. The distance between the two limit positions during the reciprocating movement of the link 30 To change the size of an oral cleaning device, the elements with large volumes in the oral cleaning device must be given priority. Currently, factors that directly affect the size of an oral cleaning device include at least the volume of the fluid pumping unit and the volume of the fluid storage unit. Since the fluid pumping unit not only needs to provide accommodation space for each moving part, but also needs to provide movement space for each moving part, link 30 can be improved from the perspective of accommodation space and movement space. In order to select the optimal distance range of the two limit positions in the reciprocating movement of link 30, the applicant conducted experiments to obtain the following experimental data for the following four sets of samples (see Figure 8) by controlling other parameters constant and only changing the distance between the two limit positions in the reciprocating movement of link 30.

[0054] Sample 1: The distance was 2.0 mm, the impact force was 0.041 N to 0.062 N, and the time required to suck up 200 ml of water was 75 to 89 seconds.

[0055] Sample 2: The distance was 2.2 mm, the impact force was 0.90 N to 0.98 N, and the time required to suck up 200 ml of water was 54 seconds to 68 seconds.

[0056] Sample 3: The distance was 2.4 mm, the impact force was 0.107 N to 0.114 N, and the time required to suck up 200 ml of water was 47 to 49 seconds.

[0057] Sample 4: The distance was 2.6 mm, the impact force was 0.127 N to 0.130 N, and the time required to suck up 200 ml of water was 40 to 43 seconds.

[0058] Here, a larger impact force indicates a stronger cleaning power, a smaller impact force indicates a weaker cleaning power, a shorter time to suck up 200ml of water means more water wasted, and a longer time means more water saved. As can be seen from the above experimental data, the greater the cleaning power, the more water is consumed, so these two conditions need to be balanced.

[0059] Furthermore, as the distance between the two limit positions of the link 30 increases during its reciprocating movement, the diaphragm sheet's ability to deform unevenly also improves, thereby increasing the amount of water inflow and outflow in the fluid pump chamber 11. The greater the amount of water outflow, the stronger the impact force of the fluid output channel 13. Based on experiments, the applicant has found that an impact force of ≥ 0.07 N already meets the needs of oral cleaning, and therefore, a standard impact force of ≥ 0.07 N can be used as the basis for subsequent experiments to determine other design parameters.

[0060] Sample 1 took a relatively long time to pump 200 ml of water, and although it could achieve the purpose of water saving, its cleaning power did not meet the requirements and could not meet the needs of oral cleaning, so it was removed.

[0061] Sample 4 had a large impact force, but the time required to pump up 200 ml of water was too short, making it unlikely that it would be able to meet the time required for one cleaning, and so it was removed.

[0062] Samples 2 and 3 were retained because the impact force was sufficient and the time required to pump up 200 ml of water was relatively reasonable.

[0063] Based on the above, in this embodiment, the two limit positions of the link 30 during its reciprocating movement are ultimately determined to be between 2.2 mm and 2.4 mm. This range not only satisfies the water flow rate per unit time and meets the standard impact force requirement, but also controls the water flow rate per unit time within a certain range, eliminating the need to increase the volume of the fluid storage unit 50. Specifically, if the distance between the two limit positions of the link 30 is less than 2.2 mm, the water flow rate will be insufficient and the water impact force requirement will not be met. If the distance between the two limit positions of the link 30 is greater than 2.4 mm, the cavity design size will be too large, which will not meet the requirement to reduce the overall design size of the shell 10. At the same time, the water flow rate per unit time will increase, requiring a larger fluid storage unit 50 to provide sufficient water storage capacity.

[0064] 2. Volume range of the fluid pump chamber 11 In this embodiment, the volume of the fluid pump chamber 11 is correlated with the flow rate of water discharged by one complete concave-convex deformation of the diaphragm sheet, so the volume of the fluid pump chamber 11 must satisfy both a sufficient flow rate per unit time and the deformation stroke of the diaphragm sheet. The flow rate per unit time of the fluid pump chamber 11 is related to the rotation speed of the motor, and in this embodiment, it is preferable to set the motor rotation speed n to 3500 mrp to 4500 mrp. If the motor rotation speed n is less than 3500 mrp, it cannot be guaranteed that the calculated flow rate per unit time of the fluid pump chamber 11 meets the requirement. If the motor rotation speed n is greater than 4500 mrp, excessive noise may be generated. The flow rate per unit time of the fluid pump chamber 11 is expressed as Q 流体ポンプ室 = nv, where Q 流体ポンプ室 is the flow rate per unit time of the fluid pump chamber 11. n is the rotation speed of the motor, i.e., the rotation speed of the eccentric wheel. v is the volume of the fluid pump chamber 11. From the above equations, the calculated flow rate per unit time of the fluid pump chamber 11 can be calculated, and when the diameter of the fluid output channel 13 is kept constant, F=10.2ρQ 流体ポンプ室The jet impact force is calculated by the formula 2 / A, where F is the jet impact force, ρ is the jet medium density, which may be water, and A may be the cross-sectional area of ​​the jet line, which includes at least the cross-sectional area of ​​the fluid output channel 13 and the nozzle for oral irrigation.

[0065] With reference to the experimental data shown in FIG.

[0066] Sample 1: The distance is 2.0 mm, and the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 Although it took a long time to pump 200 ml of water, the impact force was only 0.041 N to 0.062 N, which did not meet the standard impact force requirements, so it was removed. Comparing Sample 1 and Sample 2, the volume of the fluid pump chamber 11 did not change, but the distance in Sample 1 was too small to ensure that the diaphragm seat could operate efficiently.

[0067] Sample 4: The distance is 2.6 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 and can meet the standard requirements for impact force. However, compared with Sample 3, Sample 3 can further reduce water usage when meeting the impact force requirements, so Sample 4 was excluded.

[0068] Figure 9 is a schematic diagram of the relationship between the impact force and the distance between the two limit positions of the link, where the dashed line corresponds to the minimum impact force and the solid line corresponds to the maximum impact force. The analysis is as follows:

[0069] Considering that the utilization rate of the fluid pump chamber 11 is restricted by the limit position of the link 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 as high a level as possible. Here, the following criteria are mainly influential. Based on whether the diaphragm sheet can completely and tightly contact the side wall when it moves to the limit distance in the direction of the fluid pump chamber 11 during the process of the link 30 completing one stroke, the following four sets of data can be obtained to ensure a high level of utilization of the fluid pump chamber 11. For example, the distance between the two limit positions of the link 30 is 2.0 mm, and the volume of the fluid pump chamber is 120 mm. 3 ~130mm 3 When the distance between the two limit positions of the link 30 is 2.2 mm, the volume of the fluid pump chamber is 120 mm. 3 ~130mm 3 When the distance between the two limit positions of the link 30 is 2.4 mm, the volume of the fluid pump chamber is 155 mm. 3 ~165mm 3 When the distance between the two limit positions of the link 30 is 2.6 mm, the volume of the fluid pump chamber is 155 mm. 3 ~165mm 3 It may be the case.

[0070] 9, the minimum impact force does not tend to increase proportionally as the distance between the two limit positions of the link 30 increases. When the distance between the two limit positions of the link 30 is in the range of 2.0 mm to 2.2 mm, the change in the minimum impact force shows a first increasing trend, when the distance is in the range of 2.2 mm to 2.4 mm, the change in the minimum impact force shows a first decreasing trend, and when the distance is in the range of 2.4 mm to 2.6 mm, the change in the minimum impact force shows a second increasing trend. The above data can be divided into the following three situations because there is a dividing point in the volume of the fluid pump chamber 11.

[0071] In the first situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3The distance between the two limit positions of the link is in the range of 2.0 mm to 2.2 mm. As the distance between the two limit positions of the link 30 increases, the impact force also increases. This directly affects the utilization rate of the fluid pump chamber 11, that is, improves the stroke of the diaphragm seat, and further increases the water inflow capacity of the fluid pump chamber 11. This also directly affects the flow rate per unit time of the fluid pump chamber 11 and increases the impact force.

[0072] In the second situation, the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 The distance between the two limit positions of the link 30 is in the range of 2.4 mm to 2.6 mm. As the distance between the two limit positions of the link 30 increases, the impact force also increases. This directly affects the utilization rate of the fluid pump chamber 11, that is, improves the stroke of the diaphragm seat, and further increases the water inflow capacity of the fluid pump chamber 11. This also directly affects the flow rate per unit time of the fluid pump chamber 11 and increases the impact force.

[0073] In the third situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 The distance between the two limit positions of the link 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 The distance between the two limit positions of the link 30 is 2.4 mm, and from the change trend, it is found that the minimum impact force decreases as the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 increase, and it is proven that the impact force does not show a tendency to increase proportionally as the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 increase.

[0074] Comparing Situation 1 and Situation 2, when the volume of the fluid pump chamber 11 is the same, as the distance between the two limit positions of the link 30 increases, the utilization rate of the fluid pump chamber 11 gradually increases. As the water output increases, the impact force also gradually increases. If the first increasing trend is smaller than the second increasing trend, if the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 are large, the impact force increases more as the distance between the two limit positions of the link 30 increases, meaning that the requirement for a larger impact force is more easily met. If the distance between the volume of the fluid pump chamber 11 and the two limit positions of the link 30 is small, meaning that the requirement for a stable impact force is more easily met. Considering Situation 3, the factors that affect the impact force are not only the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11, but also the influence of other factors.

[0075] As can be seen from the solid line in Figure 9, the maximum impact force does not tend to increase proportionally as the distance between the two limit positions of link 30 increases. When the distance between the two limit positions of link 30 is in the range of 2.0mm to 2.2mm, the change in the maximum impact force shows a third increasing trend, when it is in the range of 2.2mm to 2.4mm, the change in the maximum impact force shows a fourth increasing trend, and when it is in the range of 2.4mm to 2.6mm, the change in the maximum impact force shows a fifth increasing trend, so that the third, fourth, and fifth increasing trends are clearly distinguished. Figure 10 is a schematic diagram of the relationship between water extraction time and the distance between the two limit positions of the link, with the dashed line corresponding to the shortest time and the solid line corresponding to the longest time. Analysis is as follows:

[0076] 10, the shortest time does not tend to decrease proportionally as the distance between the two limit positions of link 30 increases. When the distance between the two limit positions of link 30 is in the range of 2.0 mm to 2.2 mm, the change in the shortest time shows a first downward trend. When the distance is in the range of 2.2 mm to 2.4 mm, the change in the shortest time shows a first upward trend. When the distance is in the range of 2.4 mm to 2.6 mm, the change in the shortest time shows a second downward trend. The shorter the water extraction time, the greater the actual flow rate of fluid pump chamber 11 per unit time, which means more water is consumed. This can be divided into the following three situations:

[0077] In the first situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 The distance between the two limit positions of the link is in the range of 2.0 mm to 2.2 mm. As the distance between the two limit positions of the link 30 increases, the shortest time becomes shorter, and the impact force also increases, corresponding to the analysis results of Figure 9 above. It can be easily determined that as the distance between the two limit positions of the link 30 increases, the flow rate per unit time of the fluid pump chamber 11 also increases, and the impact force increases, verifying the above analysis.

[0078] In the second situation, the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 The distance between the two limit positions of the link 30 is in the range of 2.4 mm to 2.6 mm. As the distance between the two limit positions of the link 30 increases, the shortest time also decreases, and the impact force also increases, corresponding to the analysis of Figure 9 above. It can be easily determined that as the distance between the two limit positions of the link 30 increases, the flow rate per unit time of the fluid pump chamber 11 also increases, and the impact force increases, thereby verifying the above analysis.

[0079] In the third situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 The distance between the two limit positions of the link 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3The distance between the two limit positions of the link 30 is 2.4 mm. Looking at the change trend, the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 increase, but the minimum time becomes longer, and a situation appears in which the minimum impact force decreases, corresponding to the analysis in Figure 9 above, and the above analysis is verified.

[0080] As can be seen from the solid line in Figure 10, the longest time does not tend to decrease proportionally as the distance between the two limit positions of link 30 increases. When the distance between the two limit positions of link 30 is in the range of 2.0 mm to 2.2 mm, the change in the longest time shows a third downward trend; when the distance is in the range of 2.2 mm to 2.4 mm, the change in the longest time shows a fourth downward trend; and when the distance is in the range of 2.4 mm to 2.6 mm, the change in the longest time shows a fifth downward trend; thus, the third, fourth, and fifth downward trends are clearly distinguished.

[0081] From the above two analysis processes, it can be seen that the water output per unit time of the fluid pump chamber 11 is a factor affecting the impact force. Overall, when the volume of the fluid pump chamber 11 is in a relatively small range, the distance between the two limit positions of the link 30 needs to be ensured to meet the requirements in order to ensure that the fluid pump chamber 11 has sufficient efficiency. And the volume of the fluid pump chamber 11 should not be too small to ensure a water output sufficient to meet the impact force requirements. When the volume of the fluid pump chamber 11 is in a relatively large range, the distance between the two limit positions of the link 30 needs to be reasonably controlled to control the actual flow rate of the fluid pump chamber 11 per unit time so as to meet the water-saving requirements.

[0082] Therefore, the volume of the fluid pump chamber 11 is 120 mm 3 If the volume of the fluid pump chamber 11 is less than 165 mm, the amount of water discharge will be insufficient, and the standard requirement for impact force cannot be met unless the cross-sectional area of ​​the water discharge is changed. 3If the volume of the fluid pump chamber 11 is larger, the amount of water discharged per unit time will be too large, and although the standard requirement for impact force can be met, the consumption of the water storage capacity in the fluid storage unit 50 will be accelerated. Increasing the volume of the fluid storage unit 50 will meet the water consumption needs, but will inevitably increase the size of the entire oral cleaning device. Therefore, if the volume of the fluid pump chamber 11 is 120 mm 3 ~165mm 3 Within this range, the standard requirements for impact force can be met, and at the same time, the flow rate per unit time of the fluid pump chamber 11 can be controlled, which further achieves the purpose of water saving and reduces the volume of the fluid storage unit 50.

[0083] The distance between the two limit deformation strokes of the diaphragm sheet corresponds to the distance between the two limit positions of the link 30 during the movement process of the link 30. Under the premise of ensuring the maximum efficiency of the fluid pump chamber 11, it can be specifically classified into at least the following two situations:

[0084] In the first situation, when the distance between the two limit positions during the reciprocating movement of the link 30 is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 ~130mm 3 As shown in Figure 3, when the second end of the link 30 moves to the limit position in the first direction, the diaphragm seat is completely and tightly pressed against the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged and the maximum efficiency of the fluid pump chamber 11 can be achieved. 3 If it is larger, when the second end of the link 30 moves to the limit position in the first direction, a gap will exist between the diaphragm seat and the side wall of the fluid pump chamber 11, reducing the efficiency of the fluid pump chamber 11.

[0085] In the second situation, when the distance between the two limit positions during the reciprocating movement of the link 30 is 2.4 mm, the volume of the fluid pump chamber 11 is 155 mm. 3 ~165mm 3As shown in Figure 3, when the second end of the link 30 moves to the limit position in the first direction, the diaphragm seat is completely and tightly pressed against the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged and the maximum efficiency of the fluid pump chamber 11 can be achieved. 3 If the distance is less than this, the side wall of the fluid pump chamber 11 and the diaphragm sheet may interfere with each other, and the diaphragm sheet may not be able to complete the deformation stroke of the limit distance of 2.4 mm.

[0086] In this embodiment, the ratio of the calculated flow rate per unit time of the fluid pumping chamber to the actual flow rate per unit time of the fluid output channel is K=Q 流体ポンプ室 / Q 流体出力チャネル 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. K is in the range of 2.93≦K≦3.75, and Q 流体ポンプ室 is the calculated flow rate per unit time in the fluid pump chamber, and Q 流体出力チャネル The actual flow rate per unit time of the fluid output channel, that is, the actual amount of water flowing out of the fluid output channel 13, can be determined.

[0087] From a large amount of experimental data, the applicant has found that the smaller the K value, the greater the amount of liquid flowing out of the fluid output channel 13 per unit time and the greater the impact force, and the greater the K value, the less the amount of liquid flowing out of the fluid output channel 13 per unit time and the smaller the impact force. Based on the standard requirements for impact force, if the K value is greater than 3.75, the impact force of the fluid output channel 13 will not meet the standard requirements for impact force, but if the K value is less than 2.93, the standard requirements for impact force can be met, but the actual flow rate per unit time will increase, resulting in excessive liquid consumption and failing to meet water-saving requirements.

[0088] Furthermore, Q 流体ポンプ室 and Q 流体出力チャネルThe difference is caused by the frictional resistance of water in the liquid pipeline, which results in pressure loss. For example, in addition to the fluid input channel 12 and fluid output channel 13 introduced in this embodiment, after the water leaves the fluid storage unit 50 or before entering the spray head 80, it also passes through components such as elbows, three-way tubes, variable diameter tubes, and valves, causing the water flow state to change suddenly, i.e., turning, accelerating, colliding, swirling, and deforming. This causes pressure loss, and the water cannot be pumped into the fluid pump chamber 11 according to the calculated data, and the water in the fluid pump chamber 11 cannot be completely discharged according to the calculated discharge volume.

[0089] 3. Range of Inner Diameter of Fluid Input Channel 12 The principle of water supply by the fluid pump chamber 11 is to pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 using negative pressure, and the inner diameter of the fluid input channel 12 affects the frictional resistance of the liquid. Through a large amount of experimental data, the applicant has found that the smaller the inner diameter of the fluid input channel 12, the greater the frictional resistance of the liquid, resulting in less liquid in the fluid pump chamber 11, a smaller actual flow rate of the fluid output channel 13, and a smaller impact force of the water flow; and the larger the inner diameter of the fluid input channel 12, the smaller the frictional resistance of the liquid, resulting in more liquid entering the fluid pump chamber 11, a larger actual flow rate of the fluid output channel 13, and a greater impact force of the water flow.

[0090] With reference to the experimental data shown in FIG.

[0091] Sample 2: The distance is 2.2 mm, and the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3When the inner diameter of the fluid input channel 12 is 2.0 mm, the actual flow rate per unit time is 174 ml / min and the impact force is 0.067 N. When the inner diameter of the fluid input channel 12 is 2.5 mm, the actual flow rate per unit time is 182 ml / min and the impact force is 0.067 N. When the inner diameter of the fluid input channel 12 is 3.0 mm, the actual flow rate per unit time is 235 ml / min and the impact force is 0.094 N. As can be seen from the above data, as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time and the impact force also increase. When the inner diameter of the fluid input channel 12 is 2.0 mm to 2.5 mm, the impact force is 0.067 N, which is 0.003 N different from the standard impact force. However, the impact of 0.003 N on the cleaning effect in actual use is negligible.

[0092] Sample 3: The distance is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~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. As can be seen from the above data, as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time and the impact force also increase.

[0093] As shown in Figure 11, the relationship between the impact force and the inner diameter of the fluid input channel is shown. Here, the solid line corresponds to the experimental data of sample 2, and the dashed line corresponds to the experimental data of sample 3. The analysis is as follows:

[0094] As can be seen from the solid line corresponding to Sample 2, as the inner diameter of the fluid input channel 12 increases, the impact force also increases, and the change in impact force does not increase proportionally 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 magnitude of the impact force remains almost constant. However, when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm, the impact force shows a tendency to increase rapidly. This is due to the many factors that limit 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 limit positions of the link 30, the volume of the fluid pump chamber 11, and the rotational speed of the motor. This example uses an example in which the inner diameter of the fluid input channel 12 is changed. As the inner diameter of the fluid input channel 12 changes, the frictional resistance of the fluid input channel 12 also decreases. Only after the frictional resistance of the fluid input channel 12 decreases to a certain threshold does the frictional resistance tend to increase rapidly. This clearly shows that, under the constraints of other factors in Sample 2, the limitation of impact force due to frictional resistance when the inner diameter of the fluid input channel 12 is 2.5 mm or less cannot be effectively overcome. Therefore, when the distance between the two limit positions of the link 30 is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 ~130mm 3 If so, the inner diameter of the fluid input channel 12 may preferably be 2.5 mm or greater.

[0095] As can be seen from the dashed line corresponding to Sample 3, the impact force increases as the inner diameter of the fluid input channel 12 increases. The first trend is observed when the inner diameter of the fluid input channel 12 is between 2.0 mm and 2.5 mm, and the second trend is observed when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm. It can be easily seen that the change in the impact force does not increase proportionally with the coefficient, but the increase in the second trend is greater than the increase in the first trend. Therefore, when the inner diameter of the fluid input channel 12 is smaller than 2.5 mm, the increase in the impact force is small, and when the inner diameter of the fluid input channel 12 is larger than 2.5 mm, the increase in the impact force is large. The distance between the two limit positions of the link 30 of Sample 3 is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm. 3 ~165mm 3Since the fluid input channel 12 can overcome a frictional resistance of 2.5 mm or less, the parameters of the link 30 and the fluid pump chamber 11 of the sample 3 do not need to take into account the frictional resistance of the fluid input channel 12.

[0096] As can be seen from a comparison of the solid line corresponding to Sample 2 and the dashed line corresponding to Sample 3 in FIG. 11 , for the same inner diameter of the fluid input channel 12, the two data points for Sample 3 are both larger than the two data points for Sample 2 in terms of the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11. However, in the range of 2.0 mm to 2.5 mm for the inner diameter of the fluid input channel 12, the impact force for Sample 3 is sometimes smaller than the impact force for Sample 2. Therefore, when the inner diameters of the fluid input channels 12 are different, the impact force for Sample 3 is always larger than the impact force for Sample 2. In other words, for the same inner diameter of the fluid input channel 12, increasing the values ​​of the above two data points does not result in a proportional increase according to the coefficient. Therefore, the inner diameters of the fluid input channels 12 corresponding to Samples 2 and 3 must be rationally selected in order to meet the impact force requirements.

[0097] For example, as can be seen from FIG. 11 , only when the inner diameter of the fluid input channel 12 is larger than 2.5 mm, the impact force of sample 2 gradually meets the basic requirement of impact force, so the inner diameter of the fluid input channel 12 corresponding to sample 2 without considering other variables is preferably larger than 2.5 mm.

[0098] As shown in Figure 12, the relationship between the flow rate per unit time of the fluid pump chamber and the inner diameter of the fluid input channel is shown. Here, the solid line corresponds to the experimental data of sample 2, and the dashed line corresponds to the experimental data of sample 3. The analysis is as follows:

[0099] As can be seen from the solid line corresponding to Sample 2, as the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pumping chamber 11 also increases, but the change in the flow rate per unit time of the fluid pumping chamber 11 does not increase proportionally 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 flow rate per unit time of the fluid pumping chamber 11 hardly changes. However, when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm, the flow rate per unit time of the fluid pumping chamber 11 shows a tendency to increase rapidly. This indicates that as the inner diameter of the fluid input channel 12 changes, the frictional resistance of the fluid input channel 12 also decreases, but only after the frictional resistance of the fluid input channel 12 decreases to a certain threshold does the tendency for a rapid increase appear. This also proves the conclusion of the analysis in Figure 11. Furthermore, it is clear that, under the constraints of other factors in Sample 2, the impact force limitation due to frictional resistance cannot be effectively overcome when the inner diameter of the fluid input channel 12 is below 2.5 mm. Therefore, when the distance between the two limit positions of the link 30 is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 ~130mm 3 If so, the inner diameter of the fluid input channel 12 may preferably be 2.5 mm or greater.

[0100] As can be seen from the dashed line corresponding to sample 3, as the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pump chamber 11 also increases. This shows a first trend when the inner diameter of the fluid input channel 12 is between 2.0 mm and 2.5 mm, and a second trend when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm. It can be easily seen that the change trend of the flow rate per unit time of the fluid pump chamber 11 does not increase proportionally with the coefficient, but rather the increase in the second trend is greater than the increase in the first trend. Therefore, when the inner diameter of the fluid input channel 12 is smaller than 2.5 mm, the increase in 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 larger than 2.5 mm, the increase in the flow rate per unit time of the fluid pump chamber 11 is large. This shows that there is a correspondence between the flow rate per unit time of the fluid pump chamber 11 and the impact force. The distance between the two limit positions of the link 30 of sample 3 is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm. 3 ~165mm 3 , and the flow rate per unit time of the fluid pump chamber 11 of Sample 3 can still show an increasing trend, which proves the analytical conclusion of Figure 11, that is, the parameters of the fluid pump chamber 11 and link 30 of Sample 3 can enable the fluid input channel 12 to overcome the friction resistance of less than 2.5 mm, so the parameters of the link 30 and fluid pump chamber 11 of Sample 3 do not need to take into account the friction resistance of the fluid input channel 12.

[0101] As can be seen from comparing the solid line corresponding to sample 2 and the dashed line corresponding to sample 3 in Figure 12, for the same inner diameter of the fluid input channel 12, when viewed from the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11, the two data for sample 3 are both larger than the two data for sample 2. However, in the range of 2.0 mm to 2.5 mm of the inner diameter of the fluid input channel 12, there are cases where the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 3 is smaller than the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 2. This proves the analytical conclusion of Figure 11, and unless the inner diameters of the fluid input channels 12 corresponding to samples 2 and 3 are selected rationally, the flow rate per unit time and impact force requirements of the fluid pump chamber 11 cannot be met.

[0102] Therefore, the inner diameter of the fluid input channel 12 needs to be reasonably selected according to the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11 to meet the standard requirements of impact force.

[0103] Preferably, the inner diameter of the fluid input channel 12 is in the range of 2.0 mm to 3.0 mm. For example, the inner diameter of the fluid input channel 12 may be 2.0 mm, 2.1 mm, 2.2 mm, or 3.0 mm. Any of the above inner diameters of the fluid input channel 12 can meet the impact force requirement while controlling the actual flow rate per unit time of the fluid output channel 13 to achieve the purpose of water conservation. 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 is too small to meet the standard impact force requirement. If the inner diameter of the fluid input channel 12 is greater than 3.0 mm, the standard impact force requirement can be met, but the actual flow rate per unit time of the fluid output channel 13 is too large to achieve the purpose of water conservation.

[0104] 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 may be 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, or 3.0 mm. The above inner diameter of the fluid input channel 12 can meet the optimal cleaning power requirements in a water-saving state and improve the cleaning effect.

[0105] In one embodiment of this embodiment, the displacement unit 40 is a diaphragm sheet. The edge of the diaphragm sheet is tightly attached to the side wall of the shell 10 facing in the second direction, and the end face of the diaphragm sheet facing in the first direction and the side wall of the shell 10 are surrounded and sealed to form a variable-volume sealed space, which is the fluid pump chamber 11. The end face of the diaphragm sheet facing in the second direction is connected to the linkage unit 20, and the diaphragm sheet can be deformed by driving the linkage unit 20 to change the volume of the fluid pump chamber 11 and further change the pressure in the fluid pump chamber 11. Referring to FIG. 3, the linkage unit 20 is exemplified by the fit between the link 30 and the eccentric wheel.

[0106] The eccentric is positioned within the shell 10 in a second direction opposite to the first direction of the diaphragm sheet. The eccentric has a rotation axis 21 that is offset from its geometric center. The eccentric is configured to rotate around the rotation axis 21, which passes through the eccentric and extends along the rotation axis of the eccentric, which is parallel to but does not overlap with the central axis of the eccentric. The geometric center of the eccentric is the central position of the eccentric's geometric shape. Therefore, when the eccentric rotates around the rotation axis 21, it performs an eccentric rotational motion.

[0107] The link 30 is located between the diaphragm sheet and the eccentric wheel, and a first end of the link 30 is rotatably connected to the eccentric wheel, and when the eccentric wheel rotates, the link 30 is driven to move back and forth along a direction perpendicular to the rotation axis 21, and the second end of the link 30 extends in a direction away from the rotation axis 21, and the diaphragm sheet moves back and forth along the first and second directions as shown in Figure 3. The first end of the link 30 can be used as a power input end, and the first end of the link 30 can rotate around the rotation center by driving the eccentric wheel, and the second end opposite to the first end can be used as a power output end, and the second end of the link 30 can move back and forth along the direction perpendicular to the rotation axis 21.

[0108] The diaphragm sheet is connected to the second end of the link 30 and extends into the fluid pump chamber 11, and the plane of the diaphragm sheet acting in the fluid pump chamber 11 is arranged parallel to the pivot axis 21. During the process of the link 30 reciprocating, the diaphragm sheet cyclically increases and decreases the volume in the fluid pump chamber 11, so as to pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 in the oral cleaning device, and provide impact fluid through the fluid output channel 13.

[0109] Specifically, the diaphragm seat, the sidewall of the fluid pump chamber 11, the check valve of the fluid input channel 12, and the check valve of the fluid output channel 13 together form a sealed space. The volume of the sealed space can be changed by the concave and convex deformation of the diaphragm seat, and the pressure in the fluid pump chamber 11 increases or decreases accordingly. When the pressure in the fluid pump chamber 11 decreases, negative pressure acts to pump liquid from the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12. When the pressure in the fluid pump chamber 11 increases, liquid is expelled from the fluid pump chamber 11 through the fluid output channel 13, forming an impulse fluid. Because the fluid pump chamber 11 must suck in and then expel liquid again, a discontinuous pulse jet is formed in the fluid output channel 13, and the water hammer pressure of the pulse jet is greater than the stagnation pressure of the continuous jet. In principle, the pulsed water flow can generate huge transient energy through the water hammer effect, thereby increasing the impact force of the impulse water flow and further improving the cleaning effect. Pulsed water flow also reduces the amount of liquid used compared to continuous water flow, reducing the volume of the fluid storage unit and the size of the aircraft.

[0110] Based on this, to meet the pressure change requirements in the fluid pump chamber 11, the distance between the two limit positions of the link 30 is set within a range of 2.1 mm to 2.6 mm, which is sufficient to effectively deform the diaphragm seat. This reduces the space required to support the movement of the link 30 within the shell 10, further reducing the design size of the shell 10 and the overall size of the aircraft. According to the technical solution of this embodiment, the rotation of the eccentric wheel drives the diaphragm seat to move back and forth via the second end of the link 30, allowing the fluid output channel 13 to form a pulse jet. This ensures impact force while saving fluid consumption, allowing the use of a smaller fluid storage unit to meet fluid consumption needs. At the same time, the distance between the two limit positions of the link 30 is set within a range of 2.1 mm to 2.6 mm, which reduces the space required to support the movement of the link 30 within the shell 10 and reduces the size of the shell 10.

[0111] In another embodiment of this embodiment, the displacement unit 40 is a piston. Unlike the previous embodiment, when the diaphragm sheet moves in a concave-convex manner, the inner wall of the shell 10 facing the first direction of the diaphragm sheet must have a corresponding concave surface. However, the piston can slide along the inner wall of the shell 10 via its edge. That is, if the end face of the piston facing the first direction is flat, the inner wall of the shell 10 can also be flat. If the end face of the piston facing the first direction is arc-shaped, the inner wall of the shell 10 can also be concave. The piston has a stronger compression capacity than the diaphragm sheet and is less likely to create a gap. The end face of the piston facing the second direction is connected to the interlocking unit 20. The principle of the piston's movement is the same as that of the diaphragm sheet, and will not be described again here.

[0112] As shown in FIGS. 1A and 2, this embodiment provides an oral cleaning device including a grip case 70, the above-mentioned fluid pumping unit, a fluid storage unit 50, and a driving mechanism.

[0113] A spray head 80 is connected to an end of the gripping case 70, a fluid pumping unit is disposed within the gripping case 70, and the spray head 80 is connected to a fluid output channel 13 of the fluid pumping unit. A fluid storage unit 50 is disposed within the gripping case 70, and a water outlet of the fluid storage unit 50 is connected to a fluid input channel 12 of the fluid pumping unit. A drive mechanism is disposed within the gripping case 70 and configured to rotationally drive an eccentric wheel of the fluid pumping unit.

[0114] The oral cleaning device in this embodiment is a water flosser, which cleans teeth using the impact force of a water flow, thereby reducing the design size of the fluid pumping unit and the amount of water used, and also reducing the size of the fluid storage unit 50 accordingly, thereby reducing the design size of the handle case 70 and improving the user experience.

[0115] In this embodiment, the diameter of the liquid outlet hole of the spray head is in the range of 0.6 mm to 0.65 mm. For example, the diameter of the liquid outlet hole of the spray head may be 0.6 mm, 0.61 mm, 0.62 mm, 0.63 mm, 0.64 mm, or 0.65 mm.

[0116] In this embodiment, the drive mechanism includes a second drive member 60, and the rotation speed of the second drive member 60 is in the range of 3500 rpm to 4500 rpm. Within this range, the calculated flow rate per unit time of the fluid pump chamber 11 can be ensured, and Q 流体ポンプ室 According to the formula =nv, Q 流体ポンプ室 is in the range of 542 ml / min to 693 ml / min, and the K value can be satisfied so that it is in the range of 2.93 to 3.75, but due to the existence of frictional resistance, the calculated flow rate per unit time of the fluid pump chamber 11 and the flow rate per unit time of the spray head 80 show a certain proportional relationship, and the larger the K value, the smaller the flow rate per unit time of the nozzle, and the more water can be saved.

[0117] In this embodiment, the volume of the fluid storage unit 50 is in the range of 50 ml to 200 ml, within which the amount of water stored in the fluid storage unit 50 is sufficient to meet the demands for cleaning teeth.

[0118] In this embodiment, the volume of the fluid storage unit 50 is 50 ml. The volume of the fluid storage unit 50 depends on the volume, and it is advantageous to reduce the volume of the fluid storage unit 50 to reduce the size of the gripping case 70.

[0119] In this embodiment, the fluid storage unit 50 is disposed below the fluid pumping unit and is located at the bottom of the gripping case 70, and a liquid inlet 51 communicating with the fluid storage unit 50 is provided on the underside of the gripping case 70. That is, the fluid storage unit 50 and the fluid pumping unit are disposed along the extension direction of the gripping case 70, and by reducing the size of the gripping case 70 in the gripping direction, the user can easily hold the gripping case 70. The liquid inlet 51 is used to refill the fluid storage unit 50 with water, and a movably provided end cap is provided on the liquid inlet 51, so that the water refilling operation can be completed simply by opening the end cap.

[0120] As shown in FIG. 1A, in this embodiment, the oral cleaning device is an all-in-one rinse-and-wash type oral cleaning device, and a brush head 90 is further provided at the end of the grip case 70.

[0121] The all-in-one oral cleaning device may be a water flosser with an all-in-one rinse, which combines the functions of a water flosser and an electric toothbrush to simultaneously clean teeth and spaces between teeth, effectively removing bacteria and food residue from the tooth surface and spaces between teeth, thereby preventing oral problems and improving oral health. For example, the frictional force of the brush head 90 can be used to remove impurities from the tooth surface, and the impact force of the spray head 80 can be used to impact the residue between teeth, achieving a good cleaning effect.

[0122] In the rinse-integrated oral irrigator of this embodiment, the fluid storage unit 50 is located at the bottom of the holding case 70, and the brush head 90 is located at the top of the holding case 70. As the gravity at the top of the holding case 70 decreases and the amount of water in the fluid storage unit 50 decreases, the center of gravity of the holding case can always be located at the central position of the holding case 70, giving the user a good gripping feeling.

[0123] The design size and water consumption of the fluid pumping unit described above can be reduced, and based on this, the size of the fluid storage unit 50 can also be reduced accordingly, thereby reducing the weight of the integrated rinse-type oral irrigator. Since users generally brush their teeth for about two minutes, they do not need to hold the device for a long time, which can improve the user's experience of use, as they do not experience stiffness in their arms or fingers.

[0124] As shown in Figures 1B and 2 to 4, the present application provides an oral cleaning device including a gripping case 70, a brush head 90, a fluid storage unit 50, a fluid pumping unit, and a drive unit.

[0125] The holding case 70 is the part that the user holds when using the oral cleaning device to clean, and houses most of the components that realize the cleaning function, such as the fluid storage unit, fluid pumping unit, and drive unit mentioned above, and further includes other pipelines, etc.

[0126] A spray head 80 and a brush head 90 are connected to an end of the grip case 70, and the spray head 80 and the brush head 90 are located on the same side of the end of the grip case 70. The brush head 90 has a plurality of contact element clusters, and each contact element cluster is made up of a plurality of contact elements, which may be brush filaments, and the spray head 80 is located between the plurality of contact element clusters. The spray head 80 is connected to a fluid pumping unit to achieve the function of rinsing between teeth, and the brush head 90 is connected to the first driving member 73 of the grip case to achieve the function of brushing teeth. Therefore, the oral cleaning device provided in this embodiment can not only achieve the function of an electric toothbrush, but also the function of a water flosser, thereby improving the oral cavity cleaning effect. The fluid storage unit 50 is disposed in the grip case 70, the water pump chamber has a fluid input channel 12 communicating with the fluid storage unit 50 and a fluid output channel 13 communicating with the spray head 80, the fluid pumping unit pumps the liquid in the fluid storage unit 50 and discharges it to the spray head 80, thereby cleaning the teeth or between the teeth. The liquid may be fresh water, mouthwash, oral care liquid, etc., and the fluid storage unit 50 is used to store the liquid.

[0127] A fluid pump chamber 11 is formed within the shell 10, and a fluid input channel 12 and a fluid output channel 13 are connected to the fluid pump chamber 11. The fluid pump chamber 11 mainly realizes liquid inflow and outflow by changes in internal pressure, and check valves can be provided in the fluid input channel 12 and the fluid output channel 13. Here, the check valve in the fluid input channel 12 allows liquid to flow from the fluid storage unit toward the fluid pump chamber 11, and the check valve in the fluid output channel 13 allows liquid to flow from the fluid pump chamber 11 to the fluid output channel 13.

[0128] Furthermore, when the pressure in the fluid pump chamber 11 increases, the liquid in the fluid pump chamber 11 flows out of the spray head 80 through the fluid output channel 13, and the check valve in 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 check valve in the fluid output channel 13 prevents the liquid in the fluid output channel 13 from flowing back into the fluid pump chamber 11.

[0129] The displacement unit 40 is movably mounted on the shell 10, and the end face of the displacement unit 40 facing in the first direction and the inner wall of the shell 10 surround and form a variable fluid pump chamber 11 with a sealed volume. In this embodiment, the edge of the displacement unit 40 can be tightly attached to the inner wall of the shell 10, so that the inner wall of the shell 10 positioned in the first direction can surround and form a sealed chamber together with the diaphragm sheet. This chamber is the fluid pump chamber 11. The displacement unit 40 is movably mounted to change the volume of the fluid pump chamber 11, and the fluid input channel 12 and the fluid output channel 13 are also positioned in the first direction and communicate with the fluid pump chamber 11. Due to the arrangement of the check valve, when the volume of the fluid pump chamber 11 changes, the pressure in the fluid pump chamber 11 can also increase or decrease, thereby using negative pressure to suck liquid from the fluid input channel 12 into the fluid pump chamber 11 or using pressure to pump liquid from the fluid pump chamber 11 to the fluid output channel 13.

[0130] As shown by the dashed arrow in Figure 3, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, with the displacement unit 40 as the boundary, and the interlocking unit 20, which drives the displacement unit 40 to move, is located in a second direction opposite to the first direction. This configuration facilitates wet / dry separation and prevents liquid from entering the movement space of the interlocking unit 20, thereby avoiding any impact on the interlocking unit 20 and other electrical components.

[0131] The linkage unit 20 is provided on the shell 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction, and the linkage unit 20 is configured to drive the displacement unit 40 to move back and forth along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber 11, pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12, and provide impact fluid through the fluid output channel 13.

[0132] 3 , the displacement unit 40 reciprocates along the first and second directions. The displacement unit 40 enters the fluid pump chamber 11 and cyclically increases and decreases the volume of the fluid pump chamber 11, thereby pumping the liquid in 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 drive unit includes a first drive member 73 and a second drive member 60 provided in the grip case 70. The first drive member 73 is configured to drive the brush head 90 to oscillate left and right to clean the teeth. The second drive member 60 is connected to the interlocking unit 20 and configured to drive the interlocking unit 20 to reciprocate the displacement unit 40. For example, the first drive member 73 may be a vibration motor that drives the brush head 90 to vibrate to achieve the function of an electric toothbrush. Here, the displacement unit 40 has two limit positions during reciprocal movement in the first direction and the second direction, the distance between the two limit positions is in the range of 2.1 mm to 2.6 mm, and the volume of the fluid pump chamber 11 is 120 mm. 3 ~165mm 3 is within the range.

[0133] Specifically, the displacement unit 40, the sidewall of the fluid pump chamber 11, the check valve of the fluid input channel 12, and the check valve of the fluid output channel 13 together form a sealed space. The movement of the displacement unit 40 can change the volume of the sealed space, causing the pressure in the fluid pump chamber 11 to increase or decrease accordingly. When the pressure in the fluid pump chamber 11 decreases, negative pressure acts to pump liquid from the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12. When the pressure in the fluid pump chamber 11 increases, liquid is expelled from the fluid pump chamber 11 through the fluid output channel 13, forming an impinging water flow. Because the fluid pump chamber 11 must suck in and then expel liquid again, 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 pulsed water flow can generate large transient energy through the water hammer effect, thereby increasing the impact force of the impinging water flow and further improving the cleaning effect. Pulsed water flow also reduces water consumption compared to continuous water flow, allowing for smaller fluid storage units and reduced aircraft size.

[0134] Based on this, the distance between the two limit positions of the displacement unit 40 is set within a range of 2.1 mm to 2.6 mm. This range is sufficient to meet the pressure change requirements in the fluid pump chamber 11, thereby reducing the space required to support the movement of the interlocking unit 20 within the shell 10, further reducing the design size of the shell 10 and the overall size of the aircraft. According to the technical solution of this embodiment, the interlocking unit 20 drives the displacement unit 40 to move back and forth, allowing the fluid output channel 13 to form a pulse jet. This ensures impact force while saving fluid consumption, allowing a smaller fluid storage unit to be used to meet fluid consumption needs. At the same time, the distance between the two limit positions of the displacement unit 40 is set within a range of 2.1 mm to 2.6 mm. This setting reduces the space required to support the movement of the interlocking unit 20 and the displacement unit 20 within the shell 10, thereby reducing the size of the shell 10.

[0135] 1B, 13, and 14, in this embodiment, a rinse handle 71 is connected to the top of the grip case 70, a brush head 90 is attached to the end of the rinse handle 71, a fluid channel 711 is provided within the rinse handle 71, and a spray head 80 is attached to the end of the rinse handle 71 and communicates with a fluid output channel 13 via the fluid channel 711. The fluid pump chamber 11 pumps liquid into the fluid channel 711 via the fluid output channel 13, and the liquid can be discharged through the spray head 80. A first driving member 73 has a power output shaft 72 protruding from the grip case 70, and the rinse handle 71 is connected to the power output shaft 72, and the cleaning operation is controlled by the power output shaft 72. The power output shaft 72 vibrates the rinse handle 71 when driven by the first driving member 73, which synchronously oscillates the brush head 90 on the top of the rinse handle 71, thereby cleaning the tooth surface. With this configuration, the rinsing handle 71 not only drives the brush head 90 to swing, but also supplies liquid to the spray head 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 the rinsing function of a water flosser, improving the user experience and the cleaning effect of the oral care device, and providing a synchronized rinsing function.

[0136] In this embodiment, the power output shaft 72 can be manufactured by processing stainless steel, specifically 303 steel or 304 steel, and the vibration motor can drive the power output shaft 72 to move back and forth relative to the gripping case 70.

[0137] 14, in this embodiment, the first driving member 73 may be a vibration motor. The power output shaft 72 is a columnar body penetrating both the upper and lower ends of the first driving member 73, and includes an axial channel 721 having an outlet communicating with the fluid channel 711 and an inlet communicating with the fluid output channel 13. The columnar body has a hollow interior cavity, and the power output shaft 72 is formed with the axial channel 721, an outlet 722, and an inlet 723. Liquid pumped from the fluid output channel 13 enters the axial channel 721 through the inlet 723 and continues to flow into the fluid channel 711 from the outlet 722. This allows the axial channel 721 of the power output shaft 72 to be directly used for liquid transportation, eliminating the need for an additional liquid pipeline connecting the fluid channel 711 and the fluid output channel 13. This allows for a more rational layout of the pipeline structure in the gripper case 70, reducing the number of fluid pipelines and saving space. Furthermore, the size of the grip case 70 can be further reduced, making it easier for the user to grip and operate, and improving the user's comfort in use.

[0138] In this embodiment, the inner wall of the axial channel 721 of the power output shaft 72 is subjected to a surface smoothing treatment, for example, by adopting a polishing process, thereby increasing the smoothness of the inner wall of the axial channel 721, which is advantageous in reducing the resistance to water flow, ensuring that the loss of water flow impact due to frictional resistance is reduced, and further ensuring that the liquid sprayed by the spray head 80 has sufficient impact force to clean the teeth or between the teeth.

[0139] To ensure a sufficient service life for the power output shaft 72, the hardness of the power output shaft 72 in this embodiment ranges from 17 to 70 Rockwell hardness HRC, and the side wall thickness is 0.3 to 1 mm. Through extensive experimentation, the applicant has found that there is a close correlation between the hardness and strength of materials, and that the hardness is determined by the resistance to plastic deformation. The higher the strength of a material, the higher the resistance to plastic deformation and the higher the hardness. Generally, the higher the hardness of a material, the more wear-resistant and brittle it becomes. Therefore, to ensure both the hardness and toughness of the power output shaft 72, it is necessary to reasonably limit the hardness of the power output shaft 72. By setting the hardness of the power output shaft 72 within the above range, the hardness of the power output shaft 72 can be ensured to meet the power output needs of the vibration motor, effectively avoiding the problem of plastic deformation caused by insufficient hardness of the power output shaft 72, and at the same time avoiding the problem of brittleness and easy breakage caused by too high hardness. Even after the axial channel 721 is opened, the power output shaft 72 can maintain good hardness and toughness, ensuring power output capacity while meeting fluid transport requirements, and ensuring the service life and operational stability of the first driving member 73.

[0140] When the power output shaft 72 moves back and forth due to the driving of the first driving member 73, the axial channel 721 also moves back and forth. Considering this, the axial channel 721 oscillates relative to the fluid output channel 13, and the relative position between the inlet 723 of the axial channel 721 and the fluid output channel 13 also changes, resulting in a gap at the connection position between the two, which is detrimental to forming a stable liquid supply relationship between the inlet 723 and the fluid output channel 13.

[0141] In order to solve the above-mentioned problems, in this embodiment, as shown in Figures 14 and 15, a connecting member 74 is provided between the inlet 723 and the fluid output channel 13, and the connecting member 74 includes a communicating cavity 741, a first end 742 toward the fluid output channel and a second end 743 toward the inlet 723, and the fluid output channel 13 extends into the first end 742 of the connecting member 74, and the inlet 723 extends to the second end 743 of the connecting member 74.

[0142] The second end 743 and the first end 742 can form a stable connection with the inlet 723 and the fluid output channel 13, respectively, without any gaps appearing at the respective connection positions.

[0143] In another embodiment, the second end 743 can swing relative to the first end 742, and when the power output shaft 72 moves, liquid can also enter the axial channel 721 through the first end 742, the communicating 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 further a stable liquid supply relationship can be formed between the fluid output channel 13 and the axial channel 721, thereby overcoming the problem of changes in the relative position between the axial channel 721 of the power output shaft 72 and the fluid output channel 13.

[0144] The coupling member 74 may be integrally molded to the fluid output channel 13 and coupled to the inlet 723 via a second end 743 .

[0145] As shown in FIG. 15, in this embodiment, the connecting member 74 has an annular groove 744 disposed around the first end 742, which provides space for deformation of the connecting member 74 and facilitates the swinging of the second end 743 relative to the first end 742.

[0146] In this embodiment, the end of the flushing handle 71 is provided with a mounting groove 75, the mounting groove 75 has a boss 751, the boss 751 is formed within the mounting groove 75 and extends toward the opening of the mounting groove 75, the boss 751 is provided with an outlet for the fluid channel 711, and the spray head 80 is attached to the boss 751, and the spray head 80 has an overflow diameter different from the outlet diameter to facilitate improving the jet impact force.

[0147] 16 , in this embodiment, 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 and distributed on the contact element carrier 901, and the contact element carrier 901 is provided with a hole passage 903 corresponding to the shape of the spray head 80. The hole passage 903 can enable the spray head 80 to be extended, and the plurality of contact element clusters 902 and the spray head 80 are arranged on the same side of the rinse handle 71, so that the functions of the toothbrush and the water flosser can be used simultaneously to facilitate cleaning of teeth.

[0148] In this embodiment, the spray head 80 has an annular boss at one end connected to the outlet, and the size of the hole passage 903 is smaller than that of the annular boss, so that the hole passage 903 can press the spray head 80 against the outlet, preventing the spray head 80 from falling off due to the water flow pressure from the outlet.

[0149] Of course, the spray head 80 and the brush head 90 may be integrally molded and attached to the attachment groove 75 .

[0150] When using the oral cleaning tool provided in this embodiment, a user holds the gripping case 70 in their hand, aligns the spray head 80 and brush head 90 with the corresponding positions on the teeth and between the teeth, and selectively uses the spray head 80 and brush head 90 to clean the teeth or between the teeth. The gripping case 70 is the main carrier on which the fluid pumping unit, fluid storage unit 50, drive unit, etc. are mounted. When the impact force of the spray head 80 is guaranteed, the volume of the fluid storage unit 50 and the size of the shell 10 can be reduced, thereby significantly reducing the size and weight of the gripping case 70 and the overall size and weight of the oral cleaning tool, allowing the user to easily clean the mouth using the oral cleaning tool and improving the user's usability.

[0151] As shown in FIG. 17 , in this embodiment, a front damping pad 761 and a rear damping pad 762 are further provided inside the holding case 70, the front damping pad 761 is fitted onto the front end of the first driving member 73, and the front end of the first driving member 73 is attached inside the holding case 70 via the front damping pad 761, and the rear damping pad 762 is fitted onto the rear end of the first driving member 73, and the rear end of the first driving member 73 is attached inside the holding case 70 via the rear damping pad 762. The first driving member 73 is fitted between the gripping case 70 via a front damping pad 761 and a rear damping pad 762. The front damping pads 761 and the rear damping pads 762 can be used to prevent the first driving member 73 from coming into direct contact with the gripping case 70. The vibration damping performance of the front damping pads 761 and the rear damping pads 762 is used to dampen the first driving member 73, preventing direct contact between the first driving member 73 and the gripping case 70. This effectively reduces the vibration transmitted from the first driving member 73 to the gripping case 70, reducing the vibration and vibration noise felt by the user when gripping the gripping case 70 and improving the user experience. In this embodiment, the fluid storage unit 50 is disposed below the fluid pumping unit and located at the bottom of the gripping case 70. A water inlet 51 communicating with the fluid storage unit 50 is provided on the underside of the gripping case 70. That is, the fluid storage unit 50 and the fluid pumping unit are arranged along the extension direction of the grip case 70, and by reducing the size of the grip case 70 in the gripping direction, the user can easily grip the grip case 70. The water inlet 51 is used to refill the fluid storage unit 50 with water, and a movably mounted end cap is provided on the water inlet 51, so that the water refilling operation can be completed simply by opening the end cap.In the oral cleaning device of this embodiment, the fluid storage unit 50 is located at the bottom of the holding case 70, and the brush head 90 is located at the top of the holding case 70, so that the gravity at the top of the holding case 70 is reduced, and as the amount of water in the fluid storage unit 50 decreases, the center of gravity of the holding case can always be located at the central position of the holding case 70, giving the user a good gripping feeling.

[0152] In addition, the fluid storage unit 50 may also be arranged on the left or right side within the gripping case 70, and by increasing the size of the fluid storage unit 50 along the length direction of the gripping case 70, the size of the fluid storage unit 50 along the width direction of the gripping case 70 can be reduced, which can be determined according to actual circumstances.

[0153] Based on the above-mentioned design size of the fluid pumping unit and reduction in water consumption, the size of the fluid storage unit 50 can also be reduced accordingly, and the weight of the oral cleaning device can also be reduced. Since the user's tooth brushing time is generally about 2 minutes, there is no need to hold it for a long time, which causes stiffness in the arms or fingers, improving the user's usability.

[0154] In one embodiment of this example, the linkage unit 20 includes an eccentric and a link 30 .

[0155] The eccentric is positioned within the shell 10 in a second direction opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 that is offset from its geometric center. The rotation axis 21 passes through the eccentric and extends along the rotation axis of the eccentric, which is parallel to but does not overlap with the central axis of the eccentric. A link 30 is positioned between the displacement unit 40 and the eccentric. A first end of the link 30 is rotatably connected to the eccentric. When the eccentric rotates, the link 30 moves back and forth along a direction perpendicular to the rotation axis 21. A second end of the link 30 extends toward the displacement unit 40 and is connected to an end face of the displacement unit 40 facing the second direction. During the reciprocating movement of the link 30, the link 30 drives the displacement unit 40 to cyclically increase and decrease the volume of the fluid pump chamber 11 with the same stroke as the link 30. This pumps water from the fluid storage unit 50 into the fluid pump chamber 11 via the fluid input channel 12 and provides impact fluid via the fluid output channel 13. Here, the second end of the link 30 has two limit positions where it approaches the pivot shaft 21 or moves away from the pivot shaft 21 during reciprocating movement, and the distance between the two limit positions is within a range of 2.1 mm to 2.6 mm.

[0156] As shown by the dashed arrow in FIG. 3, the fluid pump chamber 11 is formed in a first direction of the displacement unit 40, with the displacement unit 40 as the boundary, and the link 30 and eccentric wheel that drive and move the displacement unit 40 are located in a second direction opposite to the first direction. This configuration facilitates the separation of dry and wet fluids, prevents liquid from entering the movement space of the link 30 and eccentric wheel, and avoids affecting the interlocking unit 20 and other electrical components.

[0157] The link 30 is provided on the shell 10 and is transmission-connected to the end face of the displacement unit 40 facing the second direction, and the link 30 is configured to drive the displacement unit 40 to move back and forth along the first direction and the second direction to cyclically increase and decrease the volume of the fluid pump chamber 11, pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12, and provide impact fluid through the fluid output channel 13.

[0158] The eccentric is positioned within the shell 10 in a second direction opposite to the first direction of the displacement unit 40. The eccentric has a rotation axis 21 that is offset from its geometric center. The eccentric is configured to rotate around the rotation axis 21, which passes through the eccentric and extends along the rotation axis of the eccentric, which is parallel to but does not overlap with the central axis of the eccentric. The geometric center of the eccentric is the central position of the eccentric's geometric shape. Therefore, when the eccentric rotates around the rotation axis 21, it performs an eccentric rotational motion.

[0159] The link 30 is located between the displacement unit 40 and the eccentric wheel, and a first end of the link 30 is rotatably connected to the eccentric wheel so that when the eccentric wheel rotates, the link 30 is driven to reciprocate along a direction perpendicular to the rotation axis 21, and a second end of the link 30 extends in a direction away from the rotation axis 21 so that the displacement unit 40 reciprocates along the first and second directions as shown in FIG. 3 . The first end of the link 30 can be used as a power input end, and the first end of the link 30 can rotate around the rotation center by driving the eccentric wheel, and the second end opposite to the first end can be used as a power output end, and the second end of the link 30 can reciprocate along a direction perpendicular to the rotation axis 21.

[0160] The displacement unit 40 is connected to the second end of the link 30 and protrudes into the fluid pump chamber 11, and the plane of the displacement unit 40 acting on the fluid pump chamber 11 is arranged parallel to the pivot axis 21. During the reciprocating movement of the link 30, the displacement unit 40 cyclically increases and decreases the volume within the fluid pump chamber 11, thereby pumping water from the fluid storage unit 50 into the fluid pump chamber 11 via the fluid input channel 12 in the oral cleaning device and providing an impinging water flow through the fluid output channel 13. The drive mechanism is arranged in the grip case 70 and includes a first drive member 73 configured to drive the brush head 90 to oscillate left and right to clean the teeth, and a second drive member configured to rotate the eccentric wheel around a rotation axis. For example, the first driving member 73 may be a vibration motor for driving the brush head 90 to vibrate in order to realize the function of an electric toothbrush, and the second driving member 60 may be a motor used for driving the rotating shaft 21 to rotate, and further driving and moving the eccentric wheel, the link 30, and the displacement unit 40 to change the volume of the fluid pump chamber 11, thereby realizing the function of a water flosser. Here, the second end of the link 30 has a limit position close to the rotating shaft 21 and a limit position far from the rotating shaft 21 during reciprocating movement, the distance between the two limit positions being within a range of 2.1 mm to 2.6 mm, and the volume of the fluid pump chamber 11 is 120 mm. 3 ~165mm 3 is within the range.

[0161] Based on this, the distance between the two limit positions of the link 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 change requirements in the fluid pump chamber 11. This reduces the space required to support the movement of the link 30 within the shell 10, further reducing the design size of the shell 10 and the overall size of the aircraft. According to the technical solution of this embodiment, the rotation of the eccentric wheel drives the displacement unit 40 to move back and forth via the second end of the link 30, allowing the fluid output channel 13 to form a pulse jet, ensuring impact force while saving fluid consumption. This allows the use of a smaller fluid storage unit to meet fluid consumption needs. At the same time, the distance between the two limit positions of the link 30 is set within a range of 2.1 mm to 2.6 mm. This configuration reduces the space required to support the movement of the link 30 within the shell 10, thereby reducing the size of the shell 10. The second driving member 60 is a brushless motor provided inside the holding case 70, and the rotary shaft 21 is the output shaft of the brushless motor, whose rotation speed is in the range of 3500 mrp to 4500 mrp. The brushless motor has excellent torque characteristics and a wide speed adjustment range, eliminating the need for a separate gearbox, further simplifying the structure and reducing the size of the holding case 70.

[0162] 3, the dashed arrows in the figure indicate the effective movement direction of the link 30, i.e., the link 30 needs to reciprocate in the first and second directions, and the two limit positions of the link 30 are located in the first and second directions, respectively. When the link 30 moves to the limit position in the first direction, the displacement unit 40 discharges the liquid in the fluid pump chamber 11. When the link 30 moves to the limit position in the second direction, there is a maximum distance between the displacement unit 40 and the fluid pump chamber 11 on the opposite side, reducing the pressure in the fluid pump chamber 11 and allowing the liquid to enter the fluid pump chamber 11 from the fluid input channel 12.

[0163] As shown in Figures 3 and 4, the edge of the displacement unit 40 is fixed to the side wall of the fluid pump chamber 11, and the displacement unit 40 and the second end of the link 30 can be connected by a screw. The displacement unit 40 can be injection molded integrally with the screw, which simplifies the structure and reduces the difficulty of assembly.

[0164] As shown in Figures 3 and 4, the shell 10 has a cavity for accommodating the eccentric wheel, and a second driving member 60 is provided at the bottom of the shell 10. The output shaft of the second driving member 60 extends into the cavity and is coupled with the eccentric wheel to form a rotating shaft 21. The second driving member can drive the eccentric wheel to rotate via the rotating shaft 21. For example, an on-axis roller pattern can be provided on the rotating shaft 21, and the eccentric wheel can be press-fitted into the on-axis roller pattern. The on-axis roller pattern can increase the friction between the rotating shaft 21 and the eccentric wheel, ensuring that the rotating shaft 21 can smoothly rotate and drive the eccentric wheel. A shaft base can be provided within the cavity, and the end of the output shaft of the second driving member 60 can extend into the shaft base, improving the stability of the rotation of the output shaft. In addition to providing accommodation space for the above components, the cavity must also provide a certain amount of movement space for the rotation of the eccentric wheel and the reciprocating movement of the first end of link 30. By setting the distance between the two limit positions of link 30 to 2.1 mm to 2.6 mm, the size of the movement space within the cavity can be limited, and based on this, the overall design size of shell 10 can be reduced.

[0165] Through extensive experimental data, the applicant has demonstrated that if the distance between the two limit positions of the link 30 is less than 2.1 mm, the pumping force will be weak, resulting in an insufficient pumped water flow rate and unable to meet the fluid impact force requirements; and if the distance between the two limit positions of the link 30 is greater than 2.6 mm, the design size of the cavity will be too large to meet the overall design size requirements of the shell 10. Therefore, the distance between the two limit positions of the link 30 is set to 2.1 mm to 2.6 mm. For example, it may be 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, 2.5 mm, or 2.6 mm.

[0166] In this embodiment, the first end of the link 30 overlaps with the geometric center of the eccentric wheel relative to the rotation center of the eccentric wheel, and the eccentric distance of the eccentric wheel is within the range of 1.05 mm to 1.3 mm. When the first end of the link 30 overlaps with the collective center of the eccentric wheel relative to the rotation center of the eccentric wheel, the movement stroke of the second end of the link is twice the eccentric distance of the eccentric wheel. If the eccentric distance of the eccentric wheel is set within the range of 1.05 mm to 1.3 mm, the distance between the two limit positions of the link 30 can be ensured to be within the range of 2.1 mm to 2.6 mm.

[0167] As shown in Figures 4 and 5, in this embodiment, the cross section of the eccentric perpendicular to the pivot axis 21 is circular. A trepanning member is provided at the first end of the link 30, with the axis of the trepanning member parallel to the pivot axis 21 and fitted over the outside of the eccentric. The eccentric has a shaft hole 201 that fits over the pivot axis 21. The eccentric is circular, and the trepanning member may also be circular. This reduces friction between the eccentric and the first end of the link 30, ensuring that the first end of the link 30 fits over the outer edge of the eccentric through the trepanning member, allowing for reciprocating circular motion. A 360° rotation of the eccentric around the pivot axis 21 constitutes one complete stroke of the link 30. It is more advantageous to control the distance between the two limit positions of the link 30 to be between 2.1 mm and 2.6 mm as the first end of the link 30 reciprocates circularly, ensuring that the displacement unit 40 can provide a stable pressure difference.

[0168] In order to further reduce the friction force between the eccentric and the trepanning, a bearing 22 can be provided between the eccentric and the link 30, the bearing 22 being fitted onto the eccentric and the trepanning being fitted onto the bearing 22, which can reduce the friction force between the eccentric and the link 30, preventing the eccentric from driving the link to rotate coaxially, and ensuring that the link 30 can move back and forth cyclically along a direction perpendicular to the rotation axis 21.

[0169] Since the center of mass of the eccentric wheel is not located on the axis of the rotating shaft 21, an unbalanced centrifugal force is generated when the eccentric wheel rotates, and the unbalanced torque generated increases the load on the output shaft of the second driving member 60, thereby increasing the frictional resistance of the shaft protrusion and the amount of heat generated.

[0170] 5, 6 and 7, in this embodiment, a balance weight 23 is connected to the eccentric, and the balance weight 23 is configured to increase the weight of the eccentric on the rotating shaft 21 to balance the torque of the eccentric during rotation. Specifically, the opposing ends of the balance weight 23 have different weights, with the heavier end located at the top of the shaft hole 201, which extends to the end face penetrating the balance weight 23, and the lighter end located at the top on the opposite side from the shaft hole 201. With this configuration, the mass on the rotating shaft 21 side can be increased, and further, since the weights of the opposing ends of the eccentric around the rotating shaft 21 are the same or nearly the same, the centrifugal forces at both ends of the eccentric are the same when the eccentric rotates. By solving the problem of imbalance in centrifugal force at both ends of the eccentric wheel, the torque of the output shaft of the second driving member 60 is balanced, making the rotation of the output shaft of the second driving member 60 more stable, reducing the frictional resistance of the shaft protrusions, and reducing the amount of heat generated. In addition, by arranging the balance weight 23 above the eccentric wheel, motion interference between the balance weight 23 and the link 30 is avoided, and interference in the transmission between the eccentric wheel and the link 30 can be avoided.

[0171] In a specific embodiment of this embodiment, the cross section of the balance weight 23 may be symmetrical, but as shown by the dashed lines in Figures 6 and 7, the balance weight 23 has an axis of symmetry. This configuration can avoid the introduction of new unbalance forces. Specifically, taking the direction shown in Figure 7 as an example, the balance weight 23 generally has two arcuate sides in the left-right direction, with the left arcuate side being shorter than the right arcuate side, and an oblique side in the up-down direction, with the oblique side sloping outward toward the right arc. As a result, the size of the right side of the balance weight 23 is larger than the size of the left side, and when the density of the balance weight 23 is equalized, i.e., the weight of the right side of the balance weight 23 is greater than the weight of the left side, the centrifugal forces on both the left and right sides are balanced when the eccentric wheel rotates.

[0172] Of course, the structure of the balance weight 23 can also be adjusted accordingly, but it is only necessary to increase the weight in the axial hole 201 of the eccentric.

[0173] In this embodiment, the eccentric wheel and balance weight 23 are integrally molded, which facilitates productivity and reduces assembly errors. Although a fastening member or the like may be used, the balance weight 23 is fixed to the eccentric wheel via a screw, for example, which makes it easy to adjust or replace the balance weight 23 thereafter.

[0174] In another embodiment of this embodiment, the second driving member 60 is a linear motor arranged in the gripping case 70, the interlocking 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, and the output shaft of the linear motor drives the displacement unit 40 to move back and forth, and applies a cyclically increasing and decreasing pressure to the fluid pump chamber 11.

[0175] In this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3 ~165mm 3The amount of liquid used per unit time of 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 of the fluid output channel 13 increases with an increase in the volume of the fluid pump chamber 11. If the pipe diameter of the fluid output channel 13 does not change, as the amount of liquid discharged per unit time increases, the impact force of the fluid also increases accordingly. The applicant has conducted a large amount of experiments and found that when the distance between the two limit positions of the link 30 is 2.2 mm to 2.4 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 ~165mm 3 It has been demonstrated that the pressure in the fluid output channel 13 not only meets the impact force requirement but also meets the fluid saving requirement. 3 If the volume of the fluid pump chamber 11 is less than 165 mm, the liquid flow rate will be too small to meet the impact force requirement. 3 A larger value can meet the impact force requirements, but if the liquid discharge amount per unit time is too large, it will accelerate the consumption of liquid in the fluid storage unit 50 and make it impossible to meet the cleaning time requirements, thereby affecting the cleaning effect.

[0176] More preferably, in this embodiment, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 , the distance between the two limit positions during the reciprocating movement of the link 30 is selected to be 2.2 mm.

[0177] For example, the volume of the fluid pump chamber 11 is 120 mm 3 , 121mm 3 , 122mm 3 , 123mm 3 ...or 130mm 33, when the second end of the link 30 moves to the limit position in the first direction, the displacement unit 40 is brought into complete contact with the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged. If the limit position is greater than 2.2 mm, motion interference occurs between the displacement unit 40 and the side wall of the fluid pump chamber 11 during the process of the second end of the link 30 moving to the limit position in the first direction.

[0178] More preferably, in this embodiment, the volume of the fluid pump chamber is 155 mm 3 ~165mm 3 If the distance between the two limit positions during the reciprocating movement of the link is within the range of 2.4 mm, the distance between the two limit positions during the reciprocating movement of the link is selected to be 2.4 mm.

[0179] For example, the volume of the fluid pump chamber 11 is 155 mm 3 , 156mm 3 , 157mm 3 , 158mm 3 ...or 165mm 3 3, when the second end of the link 30 moves to the limit position in the first direction, the displacement unit 40 is brought into complete contact with the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged. If the limit position is less than 2.4 mm, when the second end of the link 30 moves to the limit position in the first direction, a gap will be present between the displacement unit 40 and the side wall of the fluid pump chamber 11, reducing the operating efficiency of the fluid pump chamber 11.

[0180] In this embodiment, the parameters of the fluid pumping unit are optimized to ensure cleaning power while allowing the fluid pumping unit to save more liquid, thereby reducing the size of the fluid storage unit in the oral cleaning device, thereby resolving the trade-off between product size and cleaning power that exists in prior art water flossers.

[0181] The principles of movement of each component of the fluid pumping unit in this embodiment have been explained above. Below, the basis for the values ​​of each parameter of the fluid pumping unit in this embodiment will be explained in detail.

[0182] 1. The distance between the two limit positions during the reciprocating movement of the link 30 To change the size of an oral cleaning device, priority should be given to the elements of the oral cleaning device that occupy a large volume. Currently, the elements that directly affect the size of an oral cleaning device include at least the volume of the fluid pumping unit and the volume of the fluid storage unit. Since the fluid pumping unit not only needs to provide accommodation space for each moving member, but also needs to provide movement space for each moving component, the link 30 can be improved in terms of accommodation space and movement space. In order to select the optimal distance range of the two limit positions in the reciprocating movement of the link 30, the applicant conducted experiments to obtain the following four sets of experimental data for samples by controlling other parameters constant and only changing the distance between the two limit positions in the reciprocating movement of the link 30 (see Figure 8).

[0183] Sample 1: The distance was 2.0 mm, the impact force was 0.041 N to 0.062 N, and the time required to suck up 200 ml of liquid was 75 seconds to 89 seconds.

[0184] Sample 2: The distance was 2.2 mm, the impact force was 0.90 N to 0.98 N, and the time required to suck up 200 ml of liquid was 54 seconds to 68 seconds.

[0185] Sample 3: The distance was 2.4 mm, the impact force was 0.107 N to 0.114 N, and the time required to suck up 200 ml of liquid was 47 to 49 seconds.

[0186] Sample 4: The distance was 2.6 mm, the impact force was 0.127 N to 0.130 N, and the time required to suck up 200 ml of liquid was 40 to 43 seconds.

[0187] Here, a larger impact force indicates a stronger cleaning power, a smaller impact force indicates a weaker cleaning power, a shorter time to suck up 200 ml of liquid indicates a greater amount of liquid wastage, and a longer time indicates a greater amount of liquid saving. As can be seen from the above experimental data, the greater the cleaning power, the more liquid is consumed, so these two conditions must be balanced.

[0188] Furthermore, as the distance between the two limit positions in the reciprocating movement of the link 30 increases, the uneven deformation ability of the displacement unit 40 also improves, thereby increasing the amount of liquid inflow and outflow in the fluid pump chamber 11. The greater the amount of liquid outflow, the stronger the impact force of the fluid output channel 13. Based on experiments, the applicant has found that an impact force of ≥ 0.07 N can already meet the needs of oral cleaning, so that the standard impact force of ≥ 0.07 N can be used as the basis for subsequent experiments to determine other design parameters.

[0189] Sample 1 took a relatively long time to pump up 200 ml of liquid, which achieved the purpose of saving liquid, but the cleaning power was not up to the required level and could not meet the needs of oral cleaning, so it was removed.

[0190] Sample 4 had a large impact force, but the time required to pump up 200 ml of liquid was too short to meet the time required for one cleaning, so it was removed.

[0191] Samples 2 and 3 were retained because the impact force was sufficient and the time required to pump up 200 ml of liquid was relatively reasonable.

[0192] Based on the above, in this embodiment, the two limit positions of the link 30 during its reciprocating movement are ultimately determined to be between 2.2 mm and 2.4 mm. This range not only satisfies the required liquid flow rate per unit time and meets the standard impact force requirement, but also allows the liquid flow rate per unit time to be controlled within a certain range, eliminating the need to increase the volume of the fluid storage unit 50. Specifically, if the distance between the two limit positions of the link 30 is less than 2.2 mm, the liquid flow rate will be insufficient and the fluid impact force requirement will not be met. If the distance between the two limit positions of the link 30 is greater than 2.4 mm, the design size of the cavity will be too large to meet the requirement of reducing the overall design size of the shell 10, and at the same time, the liquid flow rate per unit time will increase, requiring a fluid storage unit 50 with a larger volume to provide sufficient liquid storage.

[0193] 2. Volume range of the fluid pump chamber 11 In this embodiment, the volume of the fluid pump chamber 11 is correlated with the flow rate of the liquid discharged by one complete concave-convex deformation of the displacement unit 40, so the volume of the fluid pump chamber 11 must satisfy both a sufficient flow rate per unit time and a deformation stroke that is compatible with 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 driving member, and in this embodiment, the rotation speed n of the second driving member is preferably set to 3500 mrp to 4500 mrp. If the rotation speed n of the second driving member is less than 3500 mrp, the requirement to meet the calculated flow rate per unit time of the fluid pump chamber 11 cannot be met, and if the rotation speed n of the second driving member is more than 4500 mrp, the noise is too loud. The flow rate per unit time of the fluid pump chamber 11 is expressed as Q 流体ポンプ室 = nv, where Q 流体ポンプ室 is the flow rate per unit time of the fluid pump chamber 11. n is the rotational speed of the second drive member, i.e., the rotational speed of the eccentric wheel. v is the volume of the fluid pump chamber 11. From the above equations, the calculated flow rate per unit time of the fluid pump chamber 11 can be calculated using the equation: F=10.2ρQ, with the diameter of the fluid output channel 13 kept constant. 流体ポンプ室The jet impact force is calculated as 2 / A, where F is the jet impact force, ρ is the jet medium density, which may be a liquid as described above, and A may be the cross-sectional area of ​​the jet line, which includes at least the cross-sectional area of ​​the fluid output channel 13 and the nozzle for oral irrigation.

[0194] With reference to the experimental data shown in FIG.

[0195] Sample 1: The distance is 2.0 mm, and the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 Although it takes a long time to pump 200 ml of liquid, the impact force is only 0.041 N to 0.062 N, which does not meet the standard requirements for impact force, so it was removed. Comparing Sample 1 and Sample 2, the volume of the fluid pump chamber 11 remains unchanged, but the distance in Sample 1 is too small to ensure that the displacement unit 40 can maintain its efficient operation.

[0196] Sample 4: The distance is 2.6 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 and can meet the standard requirements for impact force. However, compared with Sample 3, Sample 3 can further reduce water usage when meeting the impact force requirements, so Sample 4 was excluded.

[0197] Figure 9 is a schematic diagram of the relationship between the impact force and the distance between the two limit positions of the link, where the dashed line corresponds to the minimum impact force and the solid line corresponds to the maximum impact force. The analysis is as follows:

[0198] Considering that the utilization rate of the fluid pump chamber 11 is restricted by the limit position of the link 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 as high a level as possible. Here, the following criteria are mainly influential. During the process of the link 30 completing one stroke, the displacement unit 40 can be completely and tightly attached to the side wall when moving to the limit distance in the direction of the fluid pump chamber 11, and the following four sets of data can be 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 link 30 is 2.0 mm, and the volume of the fluid pump chamber is 120 mm. 3 ~130mm 3 When the distance between the two limit positions of the link 30 is 2.2 mm, the volume of the fluid pump chamber is 120 mm. 3 ~130mm 3 When the distance between the two limit positions of the link 30 is 2.4 mm, the volume of the fluid pump chamber is 155 mm. 3 ~165mm 3 When the distance between the two limit positions of the link 30 is 2.6 mm, the volume of the fluid pump chamber is 155 mm. 3 ~165mm 3 It may be the case.

[0199] 9, the minimum impact force does not tend to increase proportionally as the distance between the two limit positions of the link 30 increases. When the distance between the two limit positions of the link 30 is in the range of 2.0 mm to 2.2 mm, the change in the minimum impact force shows a first increasing trend, when the distance is in the range of 2.2 mm to 2.4 mm, the change in the minimum impact force shows a first decreasing trend, and when the distance is in the range of 2.4 mm to 2.6 mm, the change in the minimum impact force shows a second increasing trend. The above data can be divided into the following three situations because there is a dividing point in the volume of the fluid pump chamber 11.

[0200] In the first situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3The distance between the two limit positions of the link is in the range of 2.0 mm to 2.2 mm. As the distance between the two limit positions of the link 30 increases, the impact force also increases. This means that as the distance between the two limit positions of the link 30 increases, it directly affects the utilization rate of the fluid pump chamber 11, that is, improves the stroke of the displacement unit 40, and further increases the liquid inflow capacity of the fluid pump chamber 11, which also directly affects the flow rate per unit time of the fluid pump chamber 11 and increases the impact force.

[0201] In the second situation, the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 The distance between the two limit positions of the link 30 is in the range of 2.4 mm to 2.6 mm. As the distance between the two limit positions of the link 30 increases, the impact force also increases. This means that as the distance between the two limit positions of the link 30 increases, it directly affects the utilization rate of the fluid pump chamber 11, that is, improves the stroke of the displacement unit 40, and further increases the liquid inflow capacity of the fluid pump chamber 11, which also directly affects the flow rate per unit time of the fluid pump chamber 11 and increases the impact force.

[0202] In the third situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 The distance between the two limit positions of the link 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 The distance between the two limit positions of the link 30 is 2.4 mm, and from the change trend, it is found that the minimum impact force decreases as the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 increase, and it is proven that the impact force does not show a tendency to increase proportionally as the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 increase.

[0203] Comparing Situation 1 and Situation 2, when the volume of the fluid pump chamber 11 is the same, as the distance between the two limit positions of the link 30 increases, the utilization rate of the fluid pump chamber 11 gradually increases. As the liquid outflow rate increases, the impact force also gradually increases. If the first increasing trend is smaller than the second increasing trend, when the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 are large, the impact force increases more as the distance between the two limit positions of the link 30 increases, meaning that the requirement for a larger impact force is more easily met. When the distance between the volume of the fluid pump chamber 11 and the two limit positions of the link 30 is small, meaning that the requirement for a stable impact force is more easily met. Considering Situation 3, the factors that affect the impact force are not only the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11, but also the influence of other factors.

[0204] As can be seen from the dashed lines in Figure 9, the maximum impact force does not tend to increase proportionally as the distance between the two limit positions of link 30 increases. When the distance between the two limit positions of link 30 is in the range of 2.0mm to 2.2mm, the change in the maximum impact force shows a third increasing trend; when the distance is in the range of 2.2mm to 2.4mm, the change in the maximum impact force shows a fourth increasing trend; and when the distance is in the range of 2.4mm to 2.6mm, the change in the maximum impact force shows a fifth increasing trend. There is a clear distinction between the third, fourth, and fifth increasing trends. Figure 10 is a schematic diagram of the relationship between the liquid extraction time and the distance between the two limit positions of the link. The dashed line corresponds to the shortest time, and the solid line corresponds to the longest time. Analysis is as follows:

[0205] 10, the shorter the extraction time, the greater the distance between the two limit positions of link 30. When the distance between the two limit positions of link 30 is between 2.0 mm and 2.2 mm, the change in the shortest time exhibits a first downward trend. When the distance between the two limit positions of link 30 is between 2.2 mm and 2.4 mm, the change in the shortest time exhibits a first upward trend. When the distance is between 2.4 mm and 2.6 mm, the change in the shortest time exhibits a second downward trend. The shorter the extraction time, the greater the actual flow rate of the fluid pump chamber 11 per unit time, which means that more liquid is consumed. This can be divided into the following three situations:

[0206] In the first situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 The distance between the two limit positions of the link is in the range of 2.0 mm to 2.2 mm. As the distance between the two limit positions of the link 30 increases, the shortest time becomes shorter, and the impact force also increases, corresponding to the analysis results of Figure 9 above. It can be easily determined that as the distance between the two limit positions of the link 30 increases, the flow rate per unit time of the fluid pump chamber 11 also increases, and the impact force increases, verifying the above analysis.

[0207] In the second situation, the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3 The distance between the two limit positions of the link 30 is in the range of 2.4 mm to 2.6 mm. As the distance between the two limit positions of the link 30 increases, the shortest time becomes shorter, and the impact force also increases, corresponding to the analysis of Figure 9 above. It can be easily determined that as the distance between the two limit positions of the link 30 increases, the flow rate per unit time of the fluid pump chamber 11 also increases, and the impact force increases, verifying the above analysis.

[0208] In the third situation, the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3 The distance between the two limit positions of the link 30 is 2.2 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~165mm 3The distance between the two limit positions of the link 30 is 2.4 mm. Looking at the change trend, the volume of the fluid pump chamber 11 and the distance between the two limit positions of the link 30 increase, but the minimum time becomes longer, and a situation appears in which the minimum impact force decreases, corresponding to the analysis in Figure 9 above, and the above analysis is verified.

[0209] As can be seen from the solid line in Figure 10, the longest time does not tend to decrease proportionally as the distance between the two limit positions of link 30 increases. When the distance between the two limit positions of link 30 is in the range of 2.0 mm to 2.2 mm, the change in the longest time shows a third downward trend; when the distance is in the range of 2.2 mm to 2.4 mm, the change in the longest time shows a fourth downward trend; and when the distance is in the range of 2.4 mm to 2.6 mm, the change in the longest time shows a fifth downward trend; there is a clear distinction between the third, fourth, and fifth downward trends.

[0210] From the above two analysis processes, it can be seen that the amount of water discharged per unit time from the fluid pump chamber 11 is a factor affecting the impact force. Overall, when the volume of the fluid pump chamber 11 is relatively small, the distance between the two limit positions of the link 30 must be sufficient to ensure that the fluid pump chamber 11 has sufficient efficiency. The volume of the fluid pump chamber 11 must not be too small to ensure that the amount of liquid discharged is sufficient to meet the impact force requirements. When the volume of the fluid pump chamber 11 is relatively large, the distance between the two limit positions of the link 30 must be reasonably controlled to control the actual flow rate of the fluid pump chamber 11 per unit time and meet the fluid saving requirements.

[0211] Therefore, the volume of the fluid pump chamber 11 is 120 mm 3 If the volume of the fluid pump chamber 11 is less than 165 mm, the amount of liquid flowing out will be insufficient, and the standard requirement for impact force cannot be met unless the cross-sectional area of ​​the liquid flowing out is changed. 3If the volume of the fluid pump chamber 11 is larger, the amount of fluid discharged per unit time will be too large, and although the standard requirement for impact force can be met, the consumption of the fluid storage capacity in the fluid storage unit 50 will be accelerated. Increasing the volume of the fluid storage unit 50 will meet the need for the amount of fluid used, but will inevitably increase the size of the entire oral cleaning device. Therefore, if the volume of the fluid pump chamber 11 is 120 mm 3 ~165mm 3 Within this range, the standard requirements for impact force can be met, and at the same time, the flow rate per unit time of the fluid pump chamber 11 can be controlled, which further achieves the purpose of saving fluid and reduces the volume of the fluid storage unit 50.

[0212] The distance between the two limit deformation strokes of the displacement unit 40 corresponds to the distance between the two limit positions of the link 30 during the movement process of the link 30. Under the premise of ensuring the maximum efficiency of the fluid pump chamber 11, it can be specifically classified into at least the following two situations:

[0213] In the first situation, when the distance between the two limit positions during the reciprocating movement of the link 30 is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 ~130mm 3 As shown in FIG. 3, when the second end of the link 30 moves to the limit position in the first direction, the displacement unit 40 is completely and tightly attached to the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged and the maximum efficiency of the fluid pump chamber 11 can be reached. 3 If it is larger, when the second end of the link 30 moves to the limit position in the first direction, a gap will exist between the displacement unit 40 and the side wall of the fluid pump chamber 11, reducing the efficiency of the fluid pump chamber 11.

[0214] In the second situation, when the distance between the two limit positions during the reciprocating movement of the link 30 is 2.4 mm, the volume of the fluid pump chamber 11 is 155 mm. 3 ~165mm 3As shown in Fig. 3, when the second end of the link 30 moves to the limit position in the first direction, the displacement unit 40 is completely and tightly attached to the side wall of the fluid pump chamber 11, so that the liquid in the fluid pump chamber 11 can be completely discharged and the maximum efficiency of the fluid pump chamber 11 can be reached. 3 If it is less than this, the side wall of the fluid pump chamber 11 and the displacement unit 40 may interfere with each other, and the displacement unit 40 may not be able to complete the deformation stroke of the limit distance of 2.4 mm.

[0215] In this embodiment, the ratio of the calculated flow rate per unit time of the fluid pumping chamber to the actual flow rate per unit time of the fluid output channel is K=Q 流体ポンプ室 / Q 流体出力チャネル 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 channel. K is in the range of 2.93≦K≦3.75, and Q 流体ポンプ室 is the calculated flow rate per unit time in the fluid pump chamber, and Q 流体出力チャネル The actual flow rate per unit time of the fluid output channel, that is, the actual amount of liquid flowing out of the fluid output channel 13, can be determined.

[0216] From a large amount of experimental data, the applicant has found that the smaller the K value, the greater the amount of liquid flowing out of the fluid output channel 13 per unit time and the greater the impact force, and the greater the K value, the less the amount of liquid flowing out of the fluid output channel 13 per unit time and the smaller the impact force. Based on the standard requirements for impact force, if the K value is greater than 3.75, the impact force of the fluid output channel 13 will not meet the standard requirements for impact force, but if the K value is less than 2.93, the standard requirements for impact force can be met, but the actual flow rate per unit time will increase, resulting in excessive liquid consumption and failing to meet the requirements for liquid conservation.

[0217] Furthermore, Q 流体ポンプ室 and Q 流体出力チャネルThe difference is caused by the frictional resistance of the liquid in the liquid pipeline, resulting in pressure loss. For example, in addition to the fluid input channel 12 and fluid output channel 13 introduced in this embodiment, the liquid also passes through components such as elbows, three-way tubes, variable-diameter tubes, and valves after leaving the fluid storage unit 50 or before entering the spray head 80, causing the liquid flow state to change suddenly, i.e., deflection, acceleration, collision, vortex, deformation, etc., resulting in pressure loss and preventing the liquid from being pumped into the fluid pump chamber 11 according to the calculated data, and preventing the liquid in the fluid pump chamber 11 from being completely discharged according to the calculated discharge amount. During the experiment, an external container can receive the actual liquid discharge amount per unit time and record the data.

[0218] 3. Range of Inner Diameter of Fluid Input Channel 12 The principle of liquid supply by the fluid pump chamber 11 is to pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 using negative pressure, and the inner diameter of the fluid input channel 12 affects the frictional resistance of the liquid. Through a large amount of experimental data, the applicant has found that the smaller the inner diameter of the fluid input channel 12, the greater the frictional resistance of the liquid, resulting in less liquid entering the fluid pump chamber 11, a smaller actual flow rate of the fluid output channel 13, and a smaller fluid impact force; and the larger the inner diameter of the fluid input channel 12, the smaller the frictional resistance of the liquid, resulting in more liquid entering the fluid pump chamber 11, a larger actual flow rate of the fluid output channel 13, and a larger fluid impact force.

[0219] With reference to the experimental data shown in FIG.

[0220] Sample 2: The distance is 2.2 mm, and the volume of the fluid pump chamber 11 is 120 mm 3 ~130mm 3When the inner diameter of the fluid input channel 12 is 2.0 mm, the actual flow rate per unit time is 174 ml / min and the impact force is 0.067 N. When the inner diameter of the fluid input channel 12 is 2.5 mm, the actual flow rate per unit time is 182 ml / min and the impact force is 0.067 N. When the inner diameter of the fluid input channel 12 is 3.0 mm, the actual flow rate per unit time is 235 ml / min and the impact force is 0.094 N. As can be seen from the above data, as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time and the impact force also increase. When the inner diameter of the fluid input channel 12 is 2.0 mm to 2.5 mm, the impact force is 0.067 N, which is 0.003 N different from the standard impact force. However, the impact of 0.003 N on the cleaning effect in actual use is negligible.

[0221] Sample 3: The distance is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm 3 ~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. As can be seen from the above data, as the inner diameter of the fluid input channel 12 increases, the actual flow rate per unit time and the impact force also increase.

[0222] As shown in Figure 11, the relationship between the impact force and the inner diameter of the fluid input channel is shown. Here, the solid line corresponds to the experimental data of sample 2, and the dashed line corresponds to the experimental data of sample 3. The analysis is as follows:

[0223] As can be seen from the solid line corresponding to Sample 2, as the inner diameter of the fluid input channel 12 increases, the impact force also increases, and the change in the impact force does not increase proportionally to the coefficient. For example, when the inner diameter of the fluid input channel 12 is in the range of 2.0 mm to 2.5 mm, the magnitude of the impact force hardly changes, but when the inner diameter is in the range of 2.5 mm to 3.0 mm, the impact force tends to increase rapidly. This is because there are many factors that limit 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 limit positions of the link 30, the volume of the fluid pump chamber 11, and the rotational speed of the second drive member. This example takes the inner diameter of the fluid input channel 12 as an example. When the inner diameter of the fluid input channel 12 changes, the frictional resistance of the fluid input channel 12 also decreases. The frictional resistance of the fluid input channel 12 decreases to a certain threshold, and only then does it tend to increase rapidly. It is clear that under the constraints of other factors in Sample 2, the impact force limitation caused by the frictional resistance cannot be effectively overcome when the inner diameter of the fluid input channel 12 is 2.5 mm or less. Therefore, when the distance between the two limit positions of the link 30 is 2.2 mm and the volume of the fluid pump chamber 11 is 120 mm, 3 ~130mm 3 If so, the inner diameter of the fluid input channel 12 may preferably be 2.5 mm or greater.

[0224] As can be seen from the dashed line corresponding to Sample 3, the impact force increases as the inner diameter of the fluid input channel 12 increases. The first trend is observed when the inner diameter of the fluid input channel 12 is between 2.0 mm and 2.5 mm, and the second trend is observed when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm. It can be easily seen that the change in the impact force does not increase proportionally with the coefficient, but the increase in the second trend is greater than the increase in the first trend. Therefore, when the inner diameter of the fluid input channel 12 is smaller than 2.5 mm, the increase in the impact force is small, and when the inner diameter of the fluid input channel 12 is larger than 2.5 mm, the increase in the impact force is large. The distance between the two limit positions of the link 30 of Sample 3 is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm. 3 ~165mm 3Since the fluid input channel 12 can overcome a frictional resistance of 2.5 mm or less, the parameters of the link 30 and the fluid pump chamber 11 of the sample 3 do not need to take into account the frictional resistance of the fluid input channel 12.

[0225] As can be seen from a comparison of the solid line corresponding to Sample 2 and the dashed line corresponding to Sample 3 in FIG. 11 , for the same inner diameter of the fluid input channel 12, the two data points for Sample 3 are both larger than the two data points for Sample 2 in terms of the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11. However, in the range of 2.0 mm to 2.5 mm for the inner diameter of the fluid input channel 12, the impact force for Sample 3 is sometimes smaller than the impact force for Sample 2. Therefore, when the inner diameters of the fluid input channels 12 are different, the impact force for Sample 3 is always larger than the impact force for Sample 2. In other words, for the same inner diameter of the fluid input channel 12, increasing the values ​​of the above two data points does not result in a proportional increase according to the coefficient. Therefore, the inner diameters of the fluid input channels 12 corresponding to Samples 2 and 3 must be rationally selected in order to meet the impact force requirements.

[0226] For example, as can be seen from FIG. 11 , only when the inner diameter of the fluid input channel 12 is larger than 2.5 mm, the impact force of sample 2 gradually meets the basic requirement of impact force, so the inner diameter of the fluid input channel 12 corresponding to sample 2 without considering other variables is preferably larger than 2.5 mm.

[0227] As shown in Figure 12, the relationship between the flow rate per unit time of the fluid pump chamber and the inner diameter of the fluid input channel is shown. Here, the solid line corresponds to the experimental data of sample 2, and the dashed line corresponds to the experimental data of sample 3. The analysis is as follows:

[0228] As can be seen from the solid line corresponding to Sample 2, as the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pumping chamber 11 also increases, but the change in the flow rate per unit time of the fluid pumping chamber 11 does not increase proportionally 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 flow rate per unit time of the fluid pumping chamber 11 hardly changes. However, when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm, the flow rate per unit time of the fluid pumping chamber 11 shows a tendency to increase rapidly. This indicates that as the inner diameter of the fluid input channel 12 changes, the frictional resistance of the fluid input channel 12 also decreases, but only after the frictional resistance of the fluid input channel 12 decreases to a certain threshold does the tendency for a rapid increase appear. This also proves the conclusion of the analysis in Figure 11. Furthermore, it is clear that, under the constraints of other factors in Sample 2, the impact force limitation due to frictional resistance cannot be effectively overcome when the inner diameter of the fluid input channel 12 is below 2.5 mm. Therefore, when the distance between the two limit positions of the link 30 is 2.2 mm, the volume of the fluid pump chamber 11 is 120 mm. 3 ~130mm 3 If so, the inner diameter of the fluid input channel 12 may preferably be 2.5 mm or greater.

[0229] As can be seen from the dashed line corresponding to sample 3, as the inner diameter of the fluid input channel 12 increases, the flow rate per unit time of the fluid pump chamber 11 also increases. This shows a first trend when the inner diameter of the fluid input channel 12 is between 2.0 mm and 2.5 mm, and a second trend when the inner diameter of the fluid input channel 12 is between 2.5 mm and 3.0 mm. It can be easily seen that the change trend of the flow rate per unit time of the fluid pump chamber 11 does not increase proportionally with the coefficient, but rather the increase in the second trend is greater than the increase in the first trend. Therefore, when the inner diameter of the fluid input channel 12 is smaller than 2.5 mm, the increase in 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 larger than 2.5 mm, the increase in the flow rate per unit time of the fluid pump chamber 11 is large. This shows that there is a correspondence between the flow rate per unit time of the fluid pump chamber 11 and the impact force. The distance between the two limit positions of the link 30 of sample 3 is 2.4 mm, and the volume of the fluid pump chamber 11 is 155 mm. 3 ~165mm 3 , and the flow rate per unit time of the fluid pump chamber 11 of Sample 3 can still show an increasing trend, which proves the analytical conclusion of Figure 11, that is, the parameters of the fluid pump chamber 11 and link 30 of Sample 3 can enable the fluid input channel 12 to overcome the friction resistance of less than 2.5 mm, so the parameters of the link 30 and fluid pump chamber 11 of Sample 3 do not need to take into account the friction resistance of the fluid input channel 12.

[0230] As can be seen from comparing the solid line corresponding to sample 2 and the dashed line corresponding to sample 3 in Figure 12, for the same inner diameter of the fluid input channel 12, when viewed from the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11, the two data for sample 3 are both larger than the two data for sample 2. However, in the range of 2.0 mm to 2.5 mm of the inner diameter of the fluid input channel 12, there are cases where the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 3 is smaller than the flow rate per unit time of the fluid pump chamber 11 corresponding to sample 2. This proves the analytical conclusion of Figure 11, and unless the inner diameters of the fluid input channels 12 corresponding to samples 2 and 3 are selected rationally, the flow rate per unit time and impact force requirements of the fluid pump chamber 11 cannot be met.

[0231] Therefore, the inner diameter of the fluid input channel 12 needs to be reasonably selected according to the distance between the two limit positions of the link 30 and the volume of the fluid pump chamber 11 to meet the standard requirements of impact force.

[0232] Preferably, the inner diameter of the fluid input channel 12 is in the range of 2.0 mm to 3.0 mm. For example, the inner diameter of the fluid input channel 12 may be 2.0 mm, 2.1 mm, 2.2 mm, or 3.0 mm. Any of the above inner diameters of the fluid input channel 12 can satisfy the impact force requirement while controlling the actual flow rate per unit time of the fluid output channel 13 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 is too small to meet the standard impact force requirement. If the inner diameter of the fluid input channel 12 is greater than 3.0 mm, the standard impact force requirement can be met, but the actual flow rate per unit time of the fluid output channel 13 is too large to achieve the purpose of saving liquid.

[0233] 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 may be 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, or 3.0 mm. These inner diameters of the fluid input channel 12 can meet the optimal cleaning power requirements in a liquid-saving state and improve the cleaning effect.

[0234] In this embodiment, the diameter of the fluid outlet hole of the spray head is in the range of 0.6 mm to 0.65 mm. For example, the diameter of the fluid outlet hole of the spray head may be 0.6 mm, 0.61 mm, 0.62 mm, 0.63 mm, 0.64 mm, or 0.65 mm.

[0235] In this embodiment, the rotation speed of the second driving member 60 is in the range of 3500 rpm to 4500 rpm, and within this range, the calculated flow rate per unit time of the fluid pump chamber 11 can be ensured, and Q 流体ポンプ室 According to the formula =nv, Q 流体ポンプ室 is in the range of 542 ml / min to 693 ml / min, and the K value can be satisfied so that it is in the range of 2.93 to 3.75, but due to the existence of frictional resistance, the calculated flow rate per unit time of the fluid pump chamber 11 and the flow rate per unit time of the spray head 80 show a certain proportional relationship, and the larger the K value, the smaller the flow rate per unit time of the nozzle, and the more the amount of liquid used can be saved.

[0236] In this embodiment, the volume of the fluid storage unit 50 is in the range of 50 ml to 200 ml, within which the amount of liquid stored in the fluid storage unit 50 can fully meet the requirements for tooth cleaning.

[0237] In this embodiment, the volume of the fluid storage unit 50 is in the range of 50 ml to 90 ml. The volume of the fluid storage unit 50 depends on the volume, and reducing the volume of the fluid storage unit 50 is advantageous for reducing the size of the gripping case 70.

[0238] In one embodiment of this embodiment, the displacement unit 40 is a diaphragm sheet. The edge of the diaphragm sheet is tightly attached to the side wall of the shell 10 facing in the second direction, and the end face of the diaphragm sheet facing in the first direction and the side wall of the shell 10 facing in the first direction are surrounded and sealed to form a volumetrically variable sealed space, which is the fluid pump chamber 11. The end face of the diaphragm sheet facing in the second direction is connected to the linkage unit 20, so that the diaphragm sheet can be deformed by driving the linkage unit 20 to change the volume of the fluid pump chamber 11 and further change the pressure in the fluid pump chamber 11. Referring to FIG. 3, the linkage unit 20 is exemplified by the fit between the link 30 and the eccentric wheel.

[0239] The eccentric is positioned within the shell 10 in a second direction opposite to the first direction of the diaphragm sheet. The eccentric has a rotation axis 21 that is offset from its geometric center. The eccentric is configured to rotate around the rotation axis 21, which passes through the eccentric and extends along the rotation axis of the eccentric, which is parallel to but does not overlap with the central axis of the eccentric. The geometric center of the eccentric is the central position of the eccentric's geometric shape. Therefore, when the eccentric rotates around the rotation axis 21, it performs an eccentric rotational motion.

[0240] The link 30 is located between the diaphragm sheet and the eccentric wheel, and a first end of the link 30 is rotatably connected to the eccentric wheel, and when the eccentric wheel rotates, the link 30 is driven to move back and forth along a direction perpendicular to the rotation axis 21, and the second end of the link 30 extends in a direction away from the rotation axis 21, and the diaphragm sheet moves back and forth along the first and second directions as shown in Figure 3. The first end of the link 30 can be used as a power input end, and the first end of the link 30 can rotate around the rotation center by driving the eccentric wheel, and the second end opposite to the first end can be used as a power output end, and the second end of the link 30 can move back and forth along the direction perpendicular to the rotation axis 21.

[0241] The diaphragm sheet is connected to the second end of the link 30 and extends into the fluid pump chamber 11, and the plane of the diaphragm sheet acting in the fluid pump chamber 11 is arranged parallel to the pivot axis 21. During the process of the link 30 reciprocating, the diaphragm sheet cyclically increases and decreases the volume in the fluid pump chamber 11, so as to pump the liquid in the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12 in the oral cleaning device, and provide impact fluid through the fluid output channel 13.

[0242] Specifically, the diaphragm seat, the sidewall of the fluid pump chamber 11, the check valve of the fluid input channel 12, and the check valve of the fluid output channel 13 together form a sealed space. The volume of the sealed space can be changed by the concave and convex deformation of the diaphragm seat, and the pressure in the fluid pump chamber 11 increases or decreases accordingly. When the pressure in the fluid pump chamber 11 decreases, negative pressure acts to pump liquid from the fluid storage unit 50 into the fluid pump chamber 11 through the fluid input channel 12. When the pressure in the fluid pump chamber 11 increases, liquid is expelled from the fluid pump chamber 11 through the fluid output channel 13, forming an impulse flow. Because the fluid pump chamber 11 must suck in and then expel liquid again, 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 pulsed water flow can generate large transient energy through the water hammer effect, which increases the impact force of the impulse water flow and further improves the cleaning effect. Pulsed water flow also reduces the amount of liquid used compared to continuous water flow, allowing for a smaller fluid storage unit volume and reduced aircraft size.

[0243] Based on this, to meet the pressure change requirements in the fluid pump chamber 11, the distance between the two limit positions of the link 30 is set within a range of 2.1 mm to 2.6 mm, which is sufficient to effectively deform the diaphragm seat. This reduces the space required to support the movement of the link 30 within the shell 10, further reducing the design size of the shell 10 and the overall size of the aircraft. According to the technical solution of this embodiment, the rotation of the eccentric wheel drives the diaphragm seat to move back and forth via the second end of the link 30, allowing the fluid output channel 13 to form a pulse jet. This ensures impact force while saving fluid consumption, allowing the use of a smaller fluid storage unit to meet fluid consumption needs. At the same time, the distance between the two limit positions of the link 30 is set within a range of 2.1 mm to 2.6 mm. This configuration reduces the space required to support the movement of the link 30 within the shell 10, thereby reducing the size of the shell 10.

[0244] In another embodiment of this embodiment, the displacement unit 40 is a piston. Unlike the previous embodiment, when the diaphragm sheet moves in a concave-convex manner, the inner wall of the shell 10 facing the first direction of the diaphragm sheet must have a corresponding concave surface. However, the piston can slide along the inner wall of the shell 10 via its edge. That is, when the end face of the piston facing the first direction is flat, the inner wall of the shell 10 can be flat. When the end face of the piston facing the first direction is arc-shaped, the inner wall of the shell 10 can be a corresponding concave surface. The piston has a stronger compression capacity than the diaphragm sheet and is less likely to create a gap. The end face of the piston facing the second direction is connected to the interlocking unit 20. The principle of the piston's movement is the same as that of the diaphragm sheet, and will not be described again here.

[0245] 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, and all such modifications and variations are included within the scope defined by the appended claims. [Explanation of symbols]

[0246] 10 shell, 11 fluid pump chamber, 12 fluid input channel, 13 fluid output channel, 20 interlocking unit, 201 axial hole, 21 pivot shaft, 22 bearing, 23 balance weight, 30 link, 40 displacement unit, 50 fluid storage unit, 51 inlet, 60 second driving member, 70 gripping case, 71 flushing handle, 711 fluid channel, 72 power output shaft, 721 axial channel, 722 outlet, 723 inlet, 73 first driving member, 74 connecting member, 741 communicating cavity, 742 first end, 743 second end, 744 annular groove, 75 mounting groove, 751 boss, 761 front damping pad, 762 rear damping pad, 80 spray head, 90 brush head, 901 contact element carrier, 902 contact element cluster, 903 hole passage.

Claims

1. 1. A fluid pumping unit for use in an oral cleaning device, comprising: a shell (10) having a fluid pump chamber (11) formed therein, a fluid input channel (12) communicating with the fluid pump chamber (11), and a fluid output channel (13); a displacement unit (40) movably mounted on the shell (10), the end surface facing the first direction being surrounded by an inner wall of the shell (10) to form the fluid pump chamber (11) with a variable sealed volume; a linkage unit (20) provided on the shell (10) and transmission-connected to an end surface of the displacement unit (40) facing the second direction, the linkage unit (20) 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), pumping liquid in 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); a drive unit that is transmission-connected to the interlocking unit (20) and drives the interlocking unit (20) to reciprocate the displacement unit (40); The displacement unit (40) has two limit positions during reciprocating movement in the first direction and the second direction, the distance between the two limit positions is in the range of 2.1 mm to 2.6 mm, and the volume of the fluid pump chamber (11) is 120 mm. ３ ~165mm ３ A fluid pumping unit characterized by being within the range of

2. The interlocking unit (20) includes an eccentric and a link (30), The eccentric wheel is located in a second direction opposite to the first direction of the displacement unit (40) in the shell (10) and has a rotation axis (21) that is offset 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 to and not overlapping with the central axis of the eccentric wheel, the link (30) is located between the displacement unit (40) and the eccentric wheel, a first end of the link (30) is rotatably connected to the eccentric wheel and drives the link (30) to reciprocate along a direction perpendicular to the rotation axis (21) when the eccentric wheel rotates, and a second end of the link (30) extends in the direction of the displacement unit (40) and 2. The fluid pumping unit of claim 1, further comprising: a link (30) connected to an end surface of the displacement unit (40) facing the second direction; a link (30) that drives the displacement unit (40) to cyclically increase and decrease the volume in the fluid pump chamber (11) with the same stroke as the link (30) during the reciprocating movement of the link (30), thereby pumping water in 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); and a second end of the link (30) that has two limit positions during the reciprocating movement, where the second end is closer to the pivot shaft (21) and where the second end is farther away from the pivot shaft (21), and the distance between the two limit positions is within a range of 2.1 mm to 2.6 mm.

3. The fluid pumping unit of claim 2, wherein the drive unit (60) is a brushless motor, the rotating shaft (21) is an output shaft of the brushless motor, and the rotation speed of the brushless motor is in the range of 3500 mrpm to 4500 mrpm.

4. The fluid pumping unit according to claim 2, characterized in that the first end of the link (30) overlaps with the geometric center of the eccentric wheel relative to the rotation center of the eccentric wheel, and the eccentric distance of the eccentric wheel is in the range of 1.05 mm to 1.3 mm.

5. 3. The fluid pumping unit according to claim 2, wherein a balance weight (23) is connected to the eccentric, and the balance weight (23) increases the weight of the eccentric at the rotation axis (21) to balance the torque during the rotation process of the eccentric.

6. The fluid pumping unit of claim 1, wherein the drive unit (60) is a linear motor, the linkage unit (20) is an 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 volume of the fluid pump chamber (11) is 120 mm ３ ~130mm ３ 7. The fluid pumping unit according to claim 1, wherein the distance between two limit positions during the reciprocating movement of the displacement unit (40) is 2.2 mm.

8. The volume of the fluid pump chamber (11) is 155 mm ３ ~165mm ３ 7. The fluid pumping unit according to claim 1, wherein the distance between two limit positions during the reciprocating movement of the displacement unit (40) is 2.4 mm.

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

11. 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) is: K=Q 流体ポンプ室 / Q 流体出力チャネル Fulfilling the relationship, 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 (13), and K is in the range of 2.93≦K≦3.75; and Q 流体ポンプ室 is the calculated flow rate per unit time of the fluid pump chamber (11), and Q 流体出力チャネル Fluid pumping unit according to any one of the preceding claims, characterized in that ≈ ...

12. The calculated flow rate per unit time of the fluid pump chamber (11) is: Q 流体ポンプ室 = nv, 12. A fluid pumping unit according to claim 11, 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. 2. The fluid pumping unit according to claim 1, wherein the displacement unit (40) is a diaphragm seat or a piston.

14. An oral cleaning device comprising the fluid pumping unit according to any one of claims 1 to 13, further comprising a gripping case (70), a fluid storage unit (50), and a drive mechanism; a spray head (80) connected to an end of the gripping case (70), the fluid pumping unit disposed in the gripping case (70), and the spray head (80) communicating with a fluid output channel (13) of the fluid pumping unit; The fluid storage unit (50) is disposed in the gripping case (70), and the outlet of the fluid storage unit (50) is connected to the fluid input channel (12) of the fluid pumping unit; The oral cleaning device is characterized in that the drive mechanism is disposed in the grip case (70) and configured to drive the eccentric wheel of the fluid pumping unit to rotate.

15. The oral cleaning tool according to claim 14, characterized in that the diameter of the liquid discharge hole of the spray head (80) is in the range of 0.6 mm to 0.65 mm.

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

17. 17. The oral cleaning device 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 device described in claim 14, characterized in that the fluid storage unit (50) is arranged below the fluid pumping unit and located at the bottom of the gripping case (70), and a liquid inlet (51) communicating with the fluid storage unit (50) is provided on the underside of the gripping case (70).

19. An oral cleaning device as described in any one of claims 14 to 18, characterized in that the oral cleaning device is an integrated rinse-type oral cleaning device, and a brush head is further provided at the end of the holding case (70).

20. a grip case (70) having a spray head (80) and a brush head (90) connected to its end; a fluid storage unit (50) disposed within the gripping case (70); a fluid pumping unit disposed within the gripping case (70); The fluid pumping unit comprises: a shell (10) having a fluid pump chamber (11), a fluid input channel (12) communicating with the fluid pump chamber (11), and a fluid output channel (13) formed therein, the shell (10) having the spray head (80) communicating with the fluid output channel (13) and the fluid storage unit (50) having a water outlet communicating with the fluid input channel (12); a displacement unit (40) movably mounted on the shell (10), the end surface facing the first direction being surrounded by an inner wall of the shell (10) to form the fluid pump chamber (11) with a variable sealed volume; a linkage unit (20) provided in the shell (10) and communicatively connected to an end surface of the displacement unit (40) facing the second direction, the linkage unit (20) 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), pumping liquid in the fluid storage unit (50) into the fluid pump chamber (11) through the fluid input channel (12), and providing an impact fluid through the fluid output channel (13); a drive unit including a first drive member (73) and a second drive member (60) arranged in the grip case (70), wherein the first drive member (73) is configured to drive the brush head (90) to oscillate left and right to clean the teeth, and the second drive member is transmission-connected to the interlocking unit (20) and configured to drive the interlocking unit (20) to reciprocate the displacement unit (40); the displacement unit (40) has two limit positions during reciprocating movement in the first direction and the second direction, and the distance between the two limit positions is within a range of 2.1 mm to 2.6 mm; The volume of the fluid pump chamber (11) is 120 mm ３ ~165mm ３ A mouthwashing device characterized by being within the range of

21. The oral cleaning device of claim 20, characterized in that a rinsing handle (71) is connected to the top of the grip case (70), the brush head (90) is attached to the end of the rinsing handle (71), a fluid channel (711) is provided within the rinsing handle (71), the spray head (80) is attached to the end of the rinsing handle (71) and is connected to the fluid output channel (13) via the fluid channel (711), the first drive member (73) has a power output shaft (72) protruding from the grip case (70), the rinsing handle (71) is connected to the power output shaft (72) and is controlled to perform a cleaning operation by the power output shaft (72).

22. The oral cleaning device described in claim 21, characterized in that the power output shaft (72) is a columnar body that penetrates both the upper and lower ends of the first drive member (73) and has an axial channel (721), the axial channel (721) having an outlet (722) that communicates with the fluid channel (711) and an inlet (723) that communicates with the fluid output channel (13).

23. An oral cleaning device as described in claim 22, characterized in that a connecting member (74) is provided between the inlet (723) and the fluid output channel (13), the connecting member (74) having a communicating cavity (741), a first end (742) toward the fluid output channel (13), and a second end (743) toward the inlet (723), the fluid output channel (13) extending to the first end (742) of the connecting member (74) and the inlet (723) extending to the second end (743) of the connecting member (74).

24. The oral cleaning device of claim 21, characterized in that the end of the rinse handle (71) is provided with a mounting groove (75), the mounting groove (75) has a boss (751) and the boss (751) is provided with an outlet for the fluid channel, the spray head (80) is attached to the boss (751), and the brush head (90) includes a contact element carrier (901) attached to the mounting groove (75), a plurality of contact element clusters (902) distributed at a distance on the contact element carrier (901), and a hole passage (903) corresponding to the shape of the spray head (80) on the contact element carrier (901), or the spray head (80) and the brush head (90) are integrally molded and attached to the mounting groove (75).

25. The interlocking unit (20) includes an eccentric and a link (30), The eccentric wheel is located in a second direction opposite to the first direction of the displacement unit (40) in the shell (10) and has a rotation axis (21) offset 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 to and not overlapping with the central axis of the eccentric wheel, the link (30) is located between the displacement unit (40) and the eccentric wheel, a first end of the link (30) is rotatably connected to the eccentric wheel and drives the link (30) to move back and forth along a direction perpendicular to the rotation axis (21) when the eccentric wheel rotates, and a second end of the link (30) extends in the direction of the displacement unit (40) and The oral cleaning device of claim 20, characterized in that the link (30) is connected to an end surface facing the second direction of the displacement unit (40), and during the reciprocating movement of the link (30), the displacement unit (40) is driven to cyclically increase or decrease the volume in the fluid pump chamber (11) with the same stroke as the link (30), thereby pumping water in 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), and the second end of the link (30) has two limit positions during the reciprocating movement, where it is closer to the pivot axis (21) or away from the pivot axis (21), and the distance between the two limit positions is in the range of 2.1 mm to 2.6 mm.

26. An oral cleaning device as described in claim 25, characterized in that the second driving member (60) is a brushless motor provided within the gripping case (70), the rotating shaft (21) is the output shaft of the brushless motor, and the rotational speed of the brushless motor is in the range of 3500 mrpm to 4500 mrpm.

27. An oral cleaning device as described in claim 25, characterized in that the first end of the link (30) overlaps with the geometric center of the eccentric wheel relative to the rotation center of the eccentric wheel, and the eccentric distance of the eccentric wheel is in the range of 1.05 mm to 1.3 mm.

28. The oral cleaning device of claim 27, characterized in that a balance weight (23) is connected to the eccentric, and the balance weight (23) increases the weight at the rotation axis (21) of the eccentric to balance the torque during the rotation process of the eccentric.

29. The oral cleaning device described in claim 20, characterized in that the second drive member (60) is a linear motor provided within the gripping case (70), the interlocking 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. An oral cleaning device as described in any one of claims 20 to 29, characterized in that the displacement unit (40) has two limit positions during its reciprocating movement in the first direction and the second direction, and the distance between the two limit positions is in the range of 2.2 mm to 2.4 mm.

31. The volume of the fluid pump chamber (11) is 120 mm ３ ~130mm ３ 31. The oral cleaning device according to claim 30, characterized in that the distance between two limit positions during the reciprocating movement of the displacement unit (40) is 2.2 mm.

32. The volume of the fluid pump chamber (11) is 155 mm ３ ~165mm ３ 31. The oral cleaning device according to claim 30, characterized in that the distance between two limit positions during the reciprocating movement of the displacement unit (40) is 2.4 mm.

33. An oral cleaning device 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. An oral cleaning device according to claim 33, characterized in that the inner diameter of the fluid input channel (12) is in the range of 2.5 mm to 3.0 mm.

35. 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) is: K=Q 流体ポンプ室 / Q 流体出力チャネル Fulfilling the relationship, 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 channel (13), and K is in the range of 2.93≦K≦3.75; and Q 流体ポンプ室 is the calculated flow rate per unit time of the fluid pump chamber (11), and Q 流体出力チャネル 30. An oral cleaning device according to any one of claims 20 to 29, characterized in that: ≈(f) is the actual flow rate per unit time of the fluid output channel (13).

36. The calculated flow rate per unit time of the fluid pump chamber (11) is: Q 流体ポンプ室 = nv, An oral cleaning device as described in claim 35, characterized in that 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 device according to claim 33, characterized in that the diameter of the fluid output hole of the spray head (80) is in the range of 0.6 mm to 0.65 mm.

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

39. 37. The oral cleaning device 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 device according to claim 20, characterized in that the displacement unit (40) is a diaphragm sheet or a piston.

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