CN219366250U - Electric drive device for liquid pump device, liquid outlet system and tooth washing device - Google Patents

Abstract

The utility model provides an electric drive device, a liquid outlet system and a tooth washing device for a liquid pump device, which comprise the following components: a mounting structure; the power source is arranged on the mounting structure; the driving mechanism comprises a driving cam and a piston seat, the driving cam is connected with the power source in a driving way so as to rotate relative to the fixed shaft of the mounting structure, the outer contour of the driving cam comprises a first stroke contour section and a second stroke contour section, the stroke movement angle corresponding to the first stroke contour section is smaller than 180 degrees, the piston seat and the piston of the liquid pump device are synchronously moved, and the piston seat is provided with a movable matching cavity for the driving cam to move; when the first stroke contour section of the driving cam is in sliding contact with one side cavity wall of the movable matching cavity, the piston performs a liquid discharging stroke. The utility model can shorten the liquid discharge stroke time of the liquid pump device and improve the impact feeling and the pulse feeling of the pulse jet flow.

Description

Electric drive device for liquid pump device, liquid outlet system and tooth washing device

Technical Field

The utility model relates to the technical field of oral cavity cleaning, in particular to an electric drive device for a liquid pump device, a liquid outlet system and a tooth washing device.

Background

With the improvement of living standard, people's consciousness of oral care is gradually improved, and the oral cavity cleaning tools on the market are more and more diversified, wherein the tooth flusher is one of the requisite small household appliances in families as a substitute of traditional dental floss. The basic working principle is that the pump body is utilized to pump water from the water tank, high-pressure pulse water flow with hundreds or thousands of times per minute is sprayed out through the nozzle to clean food residues, dental plaque, massage gingiva and the like in tooth gaps, and the oral cavity environment is improved.

The impact force and the impulse feel of the tooth flusher are two important performance indexes. Under the condition of the same stroke, how to obtain stronger impact force and impulse feel is a subject worthy of research in the current water pump field of the tooth irrigator.

Disclosure of Invention

In view of the above-mentioned drawbacks of the prior art, the present utility model is to provide an electric driving device, a liquid outlet system and a tooth cleaning device for a liquid pump device, which can shorten the liquid outlet stroke time of the liquid pump device and improve the impact feeling and the pulse feeling of pulse jet.

In order to solve the above technical problem, the present utility model provides an electric driving device for a liquid pump device, including:

a mounting structure;

the power source is arranged on the mounting structure;

the driving mechanism comprises a driving cam and a piston seat, the driving cam is connected with the power source in a driving way so as to rotate relative to the fixed shaft of the mounting structure, the outer contour of the driving cam comprises a first stroke contour section and a second stroke contour section, the stroke movement angle corresponding to the first stroke contour section is smaller than 180 degrees, the piston seat is connected with a piston of the liquid pump device and drives the piston to synchronously move, and the piston seat is provided with a movable matching cavity for the driving cam to move;

when the first stroke contour section of the driving cam is in sliding contact with one side cavity wall of the movable matching cavity, the piston performs a liquid discharging stroke; when the second stroke contour section of the driving cam is in sliding contact with one side cavity wall of the movable matching cavity, the piston performs one of stopping movement, retarding movement and reversing movement.

Preferably, the sum of the minimum radius of curvature of the drive cam and the maximum radius of curvature of the drive cam is adapted to the spacing of the two side chamber walls of the movable mating chamber in the reciprocating direction of the piston.

Preferably, the transmission mechanism further comprises a driving gear and a driven gear which are meshed with each other, the driving gear is coaxially arranged at the driving end of the power source, the rotation axis of the driven gear is perpendicular to the rotation axis of the driving gear, and the driven gear and the driving cam are coaxially and fixedly connected.

Preferably, the transmission mechanism further comprises a rotating shaft allowing the driven gear to be sleeved, the rotating shaft is arranged on the mounting structure, the piston seat further comprises an avoidance hole allowing the rotating shaft to penetrate, and the avoidance hole is communicated with the movable fit cavity.

Preferably, the driving cam has a clamping hole, and the driven gear has a clamping protrusion which is matched with the clamping hole in a clamping way.

Preferably, the second stroke profile section includes a near stroke profile section for one of stopping, retarding and reversing the movement of the piston before the piston is in the drain stroke and after the piston is in the suction stroke, and a far stroke profile section for one of stopping, retarding and reversing the movement of the piston after the piston is in the drain stroke and before the piston is in the suction stroke.

Preferably, the piston seat comprises a piston seat body and a wear-resistant bushing, wherein the piston seat body is provided with a containing cavity, and the wear-resistant bushing is arranged in the containing cavity and is in sliding abutting fit with the driving cam.

Preferably, the piston seat comprises a piston seat body, and a connecting pipe sleeve allowing the piston of the liquid pump device to extend into and be connected with the piston seat body is arranged on the piston seat body.

The utility model also provides a liquid outlet system, comprising:

the liquid pump device comprises a pump shell, a liquid pump cavity and a piston, wherein the liquid pump cavity is arranged on the pump shell, and the piston is arranged in the pump cavity of the liquid pump cavity in a reciprocating manner;

the liquid inlet channel is communicated with the pump cavity through a liquid inlet one-way valve;

the liquid outlet channel is communicated with the pump cavity through a liquid outlet one-way valve;

the electric driving device for the liquid pump device is characterized in that the mounting structure is formed on the pump shell.

The present utility model also provides a dental irrigator comprising:

the liquid outlet system;

the nozzle is communicated with the liquid outlet flow passage;

the liquid storage tank is communicated with the liquid inlet flow channel.

As described above, the electric drive device, the liquid outlet system and the tooth irrigator for the liquid pump device have the following beneficial effects: the main innovation point is that the transmission mechanism, in particular to a driving cam of the transmission mechanism, and the outer contour of the driving cam comprises a first travel contour section and a second travel contour section. Because the driving cam is positioned in the movable matching cavity of the piston seat and can rotate relative to the fixed shaft of the mounting structure under the driving of the power source, when the first travel profile section of the driving cam is in sliding contact with one side cavity wall of the movable matching cavity, the piston performs a liquid discharge stroke; when the first stroke contour segment of the driving cam is in sliding contact with the cavity wall on the other side opposite to the movable matching cavity, the piston performs a suction stroke. It is emphasized that: the stroke movement angle alpha corresponding to the first stroke contour section is smaller than 180 degrees, so that the driving cam rotates for less than 180 degrees, the piston can complete the liquid discharging stroke, and the time of the liquid discharging stroke is reduced to be less than one half of the rotation period of the driving cam. When the second stroke contour section of the driving cam is in sliding contact with the side cavity wall of the movable matching cavity, and when the curvature radius of the second stroke contour section is equal to the base radius of the driving cam, the driving cam cannot apply force to the piston along the reciprocating direction of the piston, and at the moment, the piston stops in the pump cavity, namely, the piston stops moving; when the curvature radius of the second stroke contour section is smaller than the base circle radius of the driving cam, the piston moves reversely; and when the curvature radius of the second stroke contour section is larger than the base circle radius of the driving cam, the piston moves slowly. Further, when the first stroke contour segment of the driving cam is in sliding contact with the cavity wall on the other side opposite to the movable fit cavity, the piston performs a suction stroke, so that the time of the suction stroke can be reduced to be less than one half of the rotation period of the driving cam. That is, compared with the crank connecting rod driving mechanism and the eccentric circle driving mechanism of the existing liquid outlet system, the electric driving device adopts the specially designed driving cam under the same stroke length and stroke frequency, so that the liquid outlet stroke time of the piston can be shortened, the maximum linear speed of the piston is further increased, and the pulse feeling of higher impact force is obtained.

Drawings

Fig. 1 is a perspective view showing a tapping system of the dental irrigator of the present utility model;

FIG. 2 shows a side view of the tapping system of FIG. 1;

FIG. 3 is a cross-sectional view taken along line A-A of FIG. 2;

FIG. 4 shows an internal block diagram of an electric drive for a liquid pump apparatus;

fig. 5 shows a perspective view of the driven gear;

fig. 6 is a perspective view showing a driving cam;

fig. 7 shows an outer contour map of the drive cam;

fig. 8 shows a diagram of the movement state of the drive cam;

FIG. 9 is a graph showing the stroke time comparison of the tapping system of the present application and the existing tapping system;

FIG. 10 shows a first embodiment of a drive cam;

FIG. 11 shows a second embodiment of a drive cam;

fig. 12 shows a third embodiment of the drive cam.

Description of element reference numerals

1. Liquid pump device

11. Liquid pump cavity

12. Piston

13. Pump cavity

14. Pump case

2. Liquid inlet one-way valve

3. Liquid inlet channel

4. Liquid outlet one-way valve

5. Liquid outlet channel

6. Electric driving device

61. Power source

62. Transmission mechanism

621. Driving cam

621a push profile section

621b ineffective profile section

621c near travel profile section

621d distance travel contour segment

621e card hole

622. Rotating shaft

623. Piston seat

623a active mating cavity

623b relief hole

623c piston seat body

623d wear resistant bushing

623e connection pipe sleeve

624. Driving gear

625. Driven gear

625a clip projection

7. Nozzle

Detailed Description

Further advantages and effects of the present utility model will become apparent to those skilled in the art from the disclosure of the present utility model, which is described by the following specific examples.

It should be understood that the structures, proportions, sizes, etc. shown in the drawings are for the purpose of understanding and reading the disclosure, and are not intended to limit the scope of the utility model, which is defined by the appended claims, but rather by the claims, unless otherwise indicated, and unless otherwise indicated, all changes in structure, proportions, or otherwise, used by those skilled in the art, are included in the spirit and scope of the utility model. Also, the terms such as "upper," "lower," "left," "right," "middle," and "a" and the like recited in the present specification are merely for descriptive purposes and are not intended to limit the scope of the utility model, but are intended to provide relative positional changes or modifications without materially altering the technical context in which the utility model may be practiced.

As shown in fig. 1, 2 and 3, the present utility model provides a liquid outlet system, comprising:

the liquid pump device 1, the liquid pump device 1 comprises a pump shell 14, a liquid pump cavity 11 and a piston 12, the liquid pump cavity 11 is arranged on the pump shell 14, and the piston 12 is arranged in a pump cavity 13 of the liquid pump cavity 11 in a reciprocating manner;

the liquid inlet channel 3, the liquid inlet channel 3 is communicated with the pump cavity 13 through the liquid inlet one-way valve 2;

the liquid outlet channel 5, the liquid outlet channel 5 is communicated with the pump cavity 13 through the liquid outlet one-way valve 4;

an electric drive 6 for a liquid pump device, the electric drive 6 is formed in a pump housing 14, and the electric drive 6 is used for reciprocating a piston 12.

In the tapping system of the utility model, when the electric drive 6 is in operation, the piston 12 reciprocates in the pump chamber 13 of the liquid pump chamber 11. During the reciprocation of the piston 12, the pump chamber 13 expands or contracts with the stroke change of the piston 12. When the piston 12 is pulled back to perform a suction stroke, the volume of the pump chamber 13 is enlarged, negative pressure is generated in the pump chamber 13, the liquid outlet one-way valve 4 is switched to a closed state, the liquid inlet one-way valve 2 is switched to an open state, and liquid sequentially flows through the liquid inlet channel 3, the liquid inlet one-way valve 2 and the pump chamber 13. When the piston 12 is pushed out to perform a liquid discharge stroke, the volume of the pump cavity 13 is reduced, positive pressure is generated in the pump cavity 13, the liquid inlet one-way valve 2 is switched to a closed state, the liquid outlet one-way valve 4 is switched to an open state due to the positive pressure, and liquid in the pump cavity 13 is sprayed after sequentially flowing through the liquid outlet one-way valve 4 and the liquid outlet flow passage 5. The main innovation of the liquid outlet system of the utility model is that the electric drive 6 can reduce the time of the liquid discharge stroke, i.e. the time of the liquid discharge stroke is less than half of a complete movement cycle of the piston 12, so that the impact force and the impulse feeling of the impulse jet can be improved.

Based on this, as shown in fig. 3 to 8, the above-described electric drive device 6 for a liquid pump device will now be specifically described: the electric drive device 6 includes:

a mounting structure;

a power source 61, the power source 61 being provided to the mounting structure;

the transmission mechanism 62, the transmission mechanism 62 includes a driving cam 621 and a piston seat 623, the driving cam 621 is connected to the power source 61 in a driving way so as to rotate in a fixed shaft relative to the installation structure, the outer contour of the driving cam 621 includes a first stroke contour section 621a and a second stroke contour section, the stroke movement angle alpha corresponding to the first stroke contour section 621a is smaller than 180 degrees, the piston seat 623 is connected with the piston 12 of the liquid pump device 1 and drives the piston 12 to synchronously move, and the piston seat 623 is provided with a movable matching cavity 623a for the driving cam 621 to move;

when the first stroke contour segment 621a of the driving cam 621 slidably abuts against one side wall of the movable engagement cavity 623a, the piston 12 performs a liquid discharge stroke; when the second stroke contour segment of the driving cam 621 slidably abuts against one side wall of the movable engagement cavity 623a, the piston 12 performs one of stopping movement, retarding movement and reversing movement.

In the electric drive device 6 of the present utility model, the mounting structure is formed in the pump case 14 of the liquid pump device 1, and the mounting structure may be integrally formed in the pump case 14. The main innovation of the electric drive 6 is the transmission 62, in particular the drive cam 621 of the transmission 62, the outer contour of the drive cam 621 comprising a first stroke contour segment 621a and a second stroke contour segment. Because the drive cam 621 is located within the movable mating cavity 623a of the piston seat 623 and is capable of being axially rotated relative to the mounting structure under the drive of the power source 61, when the first stroke contour segment 621a of the drive cam 621 slidably abuts against one side wall of the movable mating cavity 623a, the piston 12 is in a liquid discharge stroke; when the first stroke contour segment 621a of the drive cam 621 slides against the opposite side wall of the movable engagement cavity 623a, the piston 12 is stroked. It is emphasized that: the first stroke profile segment 621a corresponds to a stroke movement angle α of less than 180 degrees, such that rotation of the drive cam 621 by less than 180 degrees results in the piston 12 completing the discharge stroke, thereby reducing the discharge stroke time to less than one half of the rotation period of the drive cam 621. When the second stroke contour segment of the driving cam 621 is slidably abutted against the side cavity wall of the movable fit cavity 623a, the driving cam cannot apply force to the piston in the reciprocating direction of the piston when the radius of curvature of the second stroke contour segment is equal to the base radius of the driving cam, and the piston is stopped in the pump cavity, i.e. the piston stops moving; when the curvature radius of the second stroke contour section is smaller than the base circle radius of the driving cam, the piston moves reversely; and when the curvature radius of the second stroke contour section is larger than the base circle radius of the driving cam, the piston moves slowly. Further, when the first stroke contour segment 621a of the driving cam 621 slides against the opposite side wall of the movable engagement cavity 623a, the piston 12 is stroked, which also reduces the time of the stroking to less than one-half of the rotational period of the driving cam 621. That is, compared with the crank link driving mechanism and the eccentric circle driving mechanism of the existing liquid discharging system, the electric driving device 6 of the present utility model adopts the specially designed driving cam 621 under the same stroke length and stroke frequency, which can shorten the liquid discharging stroke time of the piston 12, further increase the maximum linear velocity of the piston 12, thereby obtaining a higher impulse feeling of impact force.

As a liquid discharge stroke time contrast mode of the liquid discharge system and the existing liquid discharge system: as shown in fig. 9, the abscissa represents the rotation angle of the driving cam 621, and the abscissa represents the actual displacement of the piston 12. Curve S1 represents the motion relationship curve corresponding to the driving cam 621 and the piston 12 of the present application, and curve S2 represents the motion relationship curve corresponding to the eccentric and the piston of the existing liquid discharging system. Fig. 9 shows: curve S2 rises all the way in the range 0-180 degrees; curve S1 extends horizontally, then at a steeper angle through curve S2, and finally still extends horizontally. This means that the piston 12 of the present application has a shorter discharge stroke time and a greater maximum velocity of the piston 12 than the pistons of the prior art discharge systems.

Therefore, the electric driving device for the liquid pump device can shorten the liquid discharge stroke time of the liquid pump device and improve the impact feeling and the pulse feeling of pulse jet flow.

As two arrangements of the driving cam 621, the rotation center point of the driving cam 621 may be coincident with the axis of the piston 12, or the rotation center point of the driving cam 621 may be offset from the axis of the piston 12.

When the rotation center point of the driving cam 621 is deviated from the axis of the piston 12, the deviation distance of the rotation center point of the driving cam 621 with respect to the axis of the piston 12 is denoted as W, and W needs to satisfy the condition that: w is greater than 0 and W is less than the maximum arm length of the piston seat 623 reacting against the drive cam 621 relative to its center of rotation. In this way, the driving cam 621 indirectly applies the pushing force to the piston 12 through the piston seat 623 during the discharging stroke, and the torque value given to the piston 12 by the pushing force due to the misalignment can satisfy the general design requirements. In addition, while the tension force indirectly applied to the piston 12 by the driving cam 621 through the piston seat 623 increases the torque at the time of return stroke of the piston 12 during the suction stroke, the tension force is small, and a large moment arm does not cause a large torque.

In order to prevent the driving cam 621 from generating a large impact force to the side walls of the movable-fit chamber 623a during rotation, the sum of the minimum radius of curvature of the driving cam 621 (i.e., the base radius of the driving cam 621) and the maximum radius of curvature of the driving cam 621 is adapted to the distance between the two side walls of the movable-fit chamber 623a in the reciprocating direction of the piston 12.

As shown in fig. 4, in order to improve the compactness of the transmission mechanism 62, the transmission mechanism 62 further includes a driving gear 624 and a driven gear 625 that are engaged with each other, the driving gear 624 is coaxially disposed at the driving end of the power source 61, the rotation axis of the driven gear 625 is perpendicular to the rotation axis of the driving gear 624, and the driven gear 625 and the driving cam 621 are coaxially fixedly connected. When the power source 61 (e.g., a motor) is operated, the power source 61 drives the driving gear 624 to rotate, the driving gear 624 drives the driven gear 625 to rotate, and the driven gear 625 drives the driving cam 621 to rotate.

As shown in fig. 4 and 8, in order to improve the overall compactness of the liquid outlet system, the driving mechanism 62 further includes a rotating shaft 622 that allows the driven gear 625 to be sleeved, the rotating shaft 622 is disposed on the mounting structure, the piston seat 623 further includes a avoiding hole 623b that allows the rotating shaft 622 to pass through, and the avoiding hole 623b is communicated with the movable matching cavity 623a.

As shown in fig. 5 and 6, in order to replace the driving cam 621, the driving cam 621 has a locking hole 621e, and the driven gear 625 has a locking protrusion 625a locked and engaged with the locking hole 621 e.

As an example of the driving cam 621 described above: as shown in fig. 7, the second stroke contour segment includes a near stroke contour segment 621c and a far stroke contour segment 621d, wherein the near stroke contour segment 621c is configured to stop, retard and reverse the movement of the piston 12 before the piston 12 is in the liquid discharge stroke and after the piston 12 is in the liquid suction stroke, and the far stroke contour segment 621d is configured to stop, retard and reverse the movement of the piston 12 after the piston 12 is in the liquid discharge stroke and before the piston 12 is in the liquid suction stroke. In addition, the outer profile of the drive cam 621 includes a dead-contour segment 621b. When the first stroke contour segment 621a of the driving cam 621 is slidably abutted against one side wall of the movable engagement cavity 623a, the ineffective contour segment 621b has no force on the piston seat 623, and the piston 12 is in a liquid discharge stroke; when the first stroke contour segment 621a of the drive cam 621 is slidably engaged against the opposite side wall of the movable engagement cavity 623a, the lost-motion contour segment 621b is still free of force against the piston seat 623, and the piston 12 is in the suction stroke. Specifically, the rotation center point of the driving cam 621 coincides with the axis of the rotating shaft 622, the stroke movement angle α corresponding to the first stroke contour segment 621a is 120 degrees, the ineffective movement angle β corresponding to the ineffective contour segment 621b is 120 degrees, the near stroke movement angle γ corresponding to the near stroke contour segment 621c is 60 degrees, and the far stroke movement angle δ corresponding to the far stroke contour segment 621d is 60 degrees.

As shown in fig. 10, as a first specific embodiment of the above-described driving cam 621: making a first base circle track of the driving cam 621 with the rotation center point C of the driving cam 621 as a center, wherein the first base circle track passes through the center point a of the near-stroke contour segment 621C; a second base circle track of the driving cam 621 is formed around the rotation center point C of the driving cam 621, and the second base circle track passes through the center point B of the long-range profile section 621 d. The radius of curvature of the near-stroke contour segment 621c, except for its center point a, is smaller than the radius R1 of the first base circle track (not readily apparent in fig. 10); the radius of curvature of the long-range profile segment 621d, except for its center point B, is greater than the radius R2 of the second base circle trace (not readily apparent in fig. 10). When the driving cam 621 rotates clockwise with the current position as the initial position, the long-stroke contour 621d applies force to the lower wall of the movable engagement chamber 623a, and the piston 12 moves downward (i.e., moves in the opposite direction with respect to the discharge stroke).

As shown in fig. 11, as a second embodiment of the above-described driving cam 621: making a first base circle track of the driving cam 621 with the rotation center point C of the driving cam 621 as a center, wherein the first base circle track passes through the center point a of the near-stroke contour segment 621C; a second base circle track of the driving cam 621 is formed around the rotation center point C of the driving cam 621, and the second base circle track passes through the center point B of the long-range profile section 621 d. The curvature radius of the near-stroke contour segment 621c except the center point A thereof is equal to the radius R1 of the first base circle track; the radius of curvature of the long-range profile segment 621d, except for its center point B, is equal to the radius R2 of the second base circle track. When the driving cam 621 rotates clockwise with the current position as the initial position, neither the short stroke contour segment 621c nor the long stroke contour segment 621d can apply force to the side wall of the movable engagement cavity 623a, and the piston 12 stops moving.

As shown in fig. 12, as a third specific embodiment of the above-described driving cam 621: making a first base circle track of the driving cam 621 with the rotation center point C of the driving cam 621 as a center, wherein the first base circle track passes through the center point a of the near-stroke contour segment 621C; a second base circle track of the driving cam 621 is formed around the rotation center point C of the driving cam 621, and the second base circle track passes through the center point B of the long-range profile section 621 d. The radius of curvature of the near-stroke contour segment 621c, except for its center point a, is greater than the radius R1 of the first base circle trace (not readily apparent in fig. 12); the radius of curvature of the long-range profile segment 621d, except for its center point B, is smaller than the radius R2 of the second base circle track (not readily apparent in fig. 12). When the driving cam 621 rotates clockwise with the current position as the initial position, the short stroke contour 621c applies force to the upper wall of the movable engagement chamber 623a, and the piston 12 moves upward (i.e., moves slowly with respect to the drain stroke).

As shown in fig. 8, in order to facilitate the contact between the piston seat 623 and the driving cam 621, and to reduce maintenance costs, a part of the structure is made of a wear-resistant material, the piston seat 623 includes a piston seat body 623c and a wear-resistant bushing 623d, the piston seat body 623c is provided with a receiving cavity, and the wear-resistant bushing 623d is disposed in the receiving cavity and slidably contacts and cooperates with the driving cam 621.

In order to move the piston seat 623 and the piston 12 synchronously, the piston seat 623 includes a piston seat body 623c, and a connecting sleeve 623e for allowing the piston 12 of the liquid pump apparatus 1 to extend into connection is provided on the piston seat body 623 c.

The present utility model also provides a dental irrigator comprising:

the liquid outlet system;

the nozzle 7 is communicated with the liquid outlet flow passage 5;

a liquid storage tank (not shown) which communicates with the liquid inlet channel 3.

The tooth washer can improve the impact feeling and impact force of pulse jet flow of a user during oral cavity cleaning, and improve the oral cavity cleaning effect.

In summary, the electric driving device, the liquid outlet system and the tooth cleaning device for the liquid pump device can shorten the liquid outlet stroke time of the liquid pump device and improve the impact feeling and the pulse feeling of pulse jet flow. Therefore, the utility model effectively overcomes various defects in the prior art and has high industrial utilization value.

The above embodiments are merely illustrative of the principles of the present utility model and its effectiveness, and are not intended to limit the utility model. Modifications and variations may be made to the above-described embodiments by those skilled in the art without departing from the spirit and scope of the utility model. Accordingly, it is intended that all equivalent modifications and variations of the utility model be covered by the claims, which are within the ordinary skill of the art, be within the spirit and scope of the present disclosure.

Claims (10)

1. An electro-motive device for a liquid pump apparatus, comprising:

a mounting structure;

a power source (61), wherein the power source (61) is arranged on the mounting structure;

the driving mechanism (62) comprises a driving cam (621) and a piston seat (623), the driving cam (621) is connected with the power source (61) in a driving way so as to rotate relative to the mounting structure in a fixed shaft way, the outer contour of the driving cam (621) comprises a first stroke contour section (621 a) and a second stroke contour section, the stroke movement angle corresponding to the first stroke contour section (621 a) is smaller than 180 degrees, the piston seat (623) is connected with the piston (12) of the liquid pump device (1) and drives the piston (12) to synchronously move, and the piston seat (623) is provided with a movable matching cavity (623 a) for the driving cam (621) to move;

when the first travel contour section (621 a) of the driving cam (621) is in sliding contact with one side cavity wall of the movable matching cavity (623 a), the piston (12) performs a liquid discharge stroke; when the second stroke contour section of the driving cam (621) is in sliding contact with one side cavity wall of the movable matching cavity (623 a), the piston (12) performs one of stopping motion, retarding motion and reversing motion.

2. An electric drive for a liquid pump apparatus as claimed in claim 1, wherein: the sum of the minimum radius of curvature of the drive cam (621) and the maximum radius of curvature of the drive cam (621) is adapted to the spacing of the two side chamber walls of the movable fit chamber (623 a) in the reciprocating direction of the piston (12).

3. An electric drive for a liquid pump apparatus as claimed in claim 1, wherein: the transmission mechanism (62) further comprises a driving gear (624) and a driven gear (625) which are meshed with each other, the driving gear (624) is coaxially arranged at the driving end of the power source (61), the rotation axis of the driven gear (625) is perpendicular to the rotation axis of the driving gear (624), and the driven gear (625) and the driving cam (621) are coaxially and fixedly connected.

4. An electro-motive device for a liquid pump apparatus as claimed in claim 3 wherein: the transmission mechanism (62) further comprises a rotating shaft (622) which is sleeved with the driven gear (625), the rotating shaft (622) is arranged on the mounting structure, the piston seat (623) further comprises an avoidance hole (623 b) which is penetrated by the rotating shaft (622), and the avoidance hole (623 b) is communicated with the movable matching cavity (623 a).

5. An electro-motive device for a liquid pump apparatus as claimed in claim 3 wherein: the driving cam (621) has a locking hole (621 e), and the driven gear (625) has a locking protrusion (625 a) that is locked and engaged with the locking hole (621 e).

6. An electric drive for a liquid pump apparatus as claimed in claim 1, wherein: the second stroke profile section includes a near stroke profile section (621 c) and a far stroke profile section (621 d), the near stroke profile section (621 c) being configured to one of stop motion, retard motion, and reverse motion of the piston (12) before the piston (12) is in a liquid discharge stroke and after the piston (12) is in a liquid suction stroke, the far stroke profile section (621 d) being configured to one of stop motion, retard motion, and reverse motion of the piston (12) after the piston (12) is in a liquid discharge stroke and before the piston (12) is in a liquid suction stroke.

7. An electric drive for a liquid pump apparatus as claimed in claim 1, wherein: the piston seat (623) comprises a piston seat body (623 c) and a wear-resistant bushing (623 d), a containing cavity is formed in the piston seat body (623 c), and the wear-resistant bushing (623 d) is arranged in the containing cavity and is in sliding abutting fit with the driving cam (621).

8. An electric drive for a liquid pump apparatus as claimed in claim 1, wherein: the piston seat (623) comprises a piston seat body (623 c), and a connecting pipe sleeve (623 e) which allows the piston (12) of the liquid pump device (1) to extend into connection is arranged on the piston seat body (623 c).

9. A liquid discharge system, characterized by: comprising the following steps:

the liquid pump device (1), the liquid pump device (1) comprises a pump shell (14), a liquid pump cavity (11) and a piston (12), the liquid pump cavity (11) is arranged on the pump shell (14), and the piston (12) is arranged in a pump cavity (13) of the liquid pump cavity (11) in a reciprocating mode;

the liquid inlet flow passage (3), the liquid inlet flow passage (3) is communicated with the pump cavity (13) through the liquid inlet one-way valve (2);

the liquid outlet channel (5), the liquid outlet channel (5) is communicated with the pump cavity (13) through the liquid outlet one-way valve (4);

an electric drive for a liquid pump apparatus according to any one of claims 1 to 8, the mounting structure being formed in the pump housing (14).

10. A dental irrigator, comprising:

the tapping system of claim 9;

a nozzle (7), wherein the nozzle (7) is communicated with the liquid outlet channel (5);

the liquid storage tank is communicated with the liquid inlet channel (3).