Slipping mechanism, liquid adding pump, putting system and household appliance

Abstract

The utility model discloses a slip mechanism, liquid adding pump, putting system and household electrical appliance, including clutch disc and clutch gear, clutch disc is fixed with at least one first bump, first bump both ends of circumferential direction have unequal thickness, clutch gear is fixed with second bump, first bump and second bump intersect and are arranged at interval, and the second bump is fixed with the clutch gear. The two circumferential ends of the first protruding block are matched with the two circumferential ends of the second protruding block in shape respectively, and the clutch disc rotates by a certain angle so that the two circumferential ends of the first protruding block can abut against the two circumferential ends of the second protruding block respectively and asynchronously. The clutch disc is additionally arranged on a traditional slipping mechanism, the two ends of the first protruding block of the clutch disc can abut against the end face of the second protruding block of the clutch gear in different states of the slipping mechanism, so that the driving gear cannot generate click sound when slipping and passes through the first protruding block, no sudden deformation exists, and the driving gear is not prone to slipping. Therefore, the service life of the slipping mechanism is greatly prolonged, and the noise of the slipping mechanism is greatly reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of dispensers, in particular to a slipping mechanism, a liquid adding pump, a dosing system and a household appliance. Background Art

[0002] A ratchet and a cantilever are a common one-way slipping mechanism. In the existing ratchet and cantilever slipping mechanism, there is a large height difference in the ratchet. When the cantilever crosses this step, there will be a large mutation in the deformation of the cantilever, and a large noise will be generated instantaneously. When continuous slipping occurs, a large "click" sound will be generated. At the same time, in the existing solution, when the cantilever slips, there is always a large mutation in its shape, which will cause the cantilever to yield and deform, and will also accelerate the wear at the top teeth of the ratchet and the cantilever, thereby reducing the service life of the slipping mechanism. Summary of the Utility Model

[0003] In order to solve the technical problem that in the existing cantilever slipping mechanism, a ratchet is used to achieve one-way slipping, when continuous slipping occurs, a large noise will be generated, and the wear at the top teeth of the ratchet and the cantilever will be accelerated, thereby reducing the service life of the slipping mechanism, the utility model provides a slipping mechanism, a liquid adding pump, a dosing system and a household appliance to solve the above problems.

[0004] The utility model provides a slipping mechanism, including a clutch disc and a clutch gear. At least one first convex block is fixed on the clutch disc, and the thicknesses of the two circumferential ends of the first convex block are unequal. A second convex block is fixed on the clutch gear. The first convex blocks and the second convex blocks are arranged in a crossed and spaced manner. The two circumferential ends of the first convex block are respectively adapted to the two circumferential ends of the second convex block in shape. The clutch disc rotates by a certain angle to make the two circumferential ends of the first convex block respectively and non-simultaneously contact with the two circumferential ends of the second convex block.

[0005] Further, the slipping mechanism further includes a driving gear. One end of the driving gear is fixed with a cantilever, and a first abutting surface is formed at the end of the cantilever. When the slipping mechanism is in the locked state, the first abutting surface abuts against one end face of the first convex block, and the thickness of this end face is greater than the thickness of the other end of the first convex block. A slipping part for radially pressing the cantilever is provided in the middle of the first convex block, so that the cantilever can drive the clutch disc to rotate by a certain angle.

[0006] Further, the two circumferential ends of the first convex block are respectively a clutch part and a locking part, and the two circumferential ends of the second convex block are respectively a combining part and an abutting part. The clutch part is opposite to the abutting part, and the locking part is opposite to the combining part. When the slipping mechanism is in the locked state, the first abutting surface abuts against the end face of the locking part.

[0007] When the driving gear rotates in the first direction, the first abutting surface, the locking portion, and the engaging portion can abut in sequence. At this time, the slipping mechanism is in the locked state, and the driving gear drives the clutch gear to rotate through the clutch disc. When the driving gear rotates in the opposite direction of the first direction, the cantilever squeezes and rubs against the slipping portion to drive the clutch disc to rotate until the locking portion of the clutch disc cooperates and docks with the engaging portion of the clutch gear, so that the cantilever smoothly transitions to the locking portion. At this time, the slipping mechanism is in the slipping state, and the driving gear cannot drive the clutch gear to rotate.

[0008] Further, the circumferential end surface of the locking portion is a stepped end surface that gradually protrudes circumferentially from the inside to the outside. When the slipping mechanism is in the locked state, the first abutting surface abuts against the end surface of the locking portion close to the inside, and the locking portion has a limiting surface that shields the outside of the cantilever.

[0009] Further, the end surface where the locking portion abuts against the first abutting surface is the second abutting surface. The second abutting surface is arranged obliquely with respect to the radial direction of the clutch gear, so that an acute angle is formed between the second abutting surface and the tangent of the limiting surface.

[0010] Further, the first abutting surface is arranged obliquely with respect to the radial direction of the driving gear, and the inclination angle is α. The inclination angle of the second abutting surface with respect to the radial direction of the clutch gear is β, then β ≤ α.

[0011] Further, 0 < α < 60, 0 < β < 60.

[0012] Further, β = 10°, α = 15°.

[0013] Further, the minimum inner diameter of the second convex block is greater than the minimum inner diameter of the first convex block.

[0014] Further, the slipping portion has a radial protrusion that radially presses the cantilever.

[0015] Further, the outer side of the free end of the cantilever has an inwardly converging transition surface, and the transition surface can pass through either side of the radial protrusion.

[0016] Further, the outer side of the cantilever has a ramp surface connected to the transition surface, and the ramp surface gradually extends radially outward from the side away from the free end of the cantilever to the side close to the free end of the cantilever.

[0017] Further, when the engaging portion cooperates and docks with the locking portion, the inner diameter of the engaging portion at the docking surface of the engaging portion and the locking portion is smaller than the inner diameter of the locking portion at this position, and is greater than the minimum inner diameter of the slipping portion.

[0018] Further, the inner side surface of the second convex block is an inclined surface that transitionally connects the engaging portion and the abutting portion.

[0019] Further, the radial distance between the arc surface where the limiting surface is located and the inner side in the radial direction of the first bump is X, and 0 < X < 1 mm.

[0020] Further, X = 0.7 mm.

[0021] Further, the first bump protrudes from the surface of the clutch disc towards the direction of the driving gear.

[0022] The present utility model further provides a liquid adding pump, which includes a driving motor and one or more than one of the above-mentioned slipping mechanisms connected to the driving motor, and the driving gear of the slipping mechanism is meshed and driven with the output end of the driving motor.

[0023] The present utility model further provides a dosing system, which includes the above-mentioned liquid adding pump.

[0024] The present utility model further provides a household appliance, which includes the above-mentioned dosing system.

[0025] The beneficial effects of the present utility model are as follows:

[0026] (1) A clutch disc is added to the traditional slipping mechanism of the present utility model, so that both ends of the first bump of the clutch disc can respectively abut against the end face of the second bump of the clutch gear in different working states of the slipping mechanism, thereby eliminating one end face of the first bump. By reasonably setting the thickness of the first bump, the driving gear will not produce a "click" sound when slipping through the first bump, and the cantilever can slip smoothly without any sudden deformation, thereby greatly improving the service life of the slipping mechanism and greatly reducing the noise of the slipping mechanism.

[0027] (2) Dot-shaped radial protrusions are arranged on the slipping part of the clutch disc of the present utility model, which can not only provide sufficient extrusion force to the cantilever, but also minimize the extrusion time of the cantilever to avoid fatigue damage of the cantilever. Description of the Drawings

[0028] The present utility model will be further described below in conjunction with the drawings and embodiments.

[0029] Figure 1 is an exploded view of the slipping mechanism described in the present utility model;

[0030] Figure 2 is a three-dimensional view of the driving gear in the present utility model;

[0031] Figure 3 is a schematic layout diagram of the cantilever in the driving gear described in the present utility model;

[0032] Figure 4 is a front view of the clutch disc in the present utility model;

[0033] Figure 5 It is a front view of the clutch gear in the utility model;

[0034] Figure 6 It is a schematic diagram of the sliding mechanism of the utility model in a locked state;

[0035] Figure 7 It is a schematic diagram of the slip mechanism of the utility model being reversed from a locked state to prepare to enter a slip state;

[0036] Figure 8 It is a schematic diagram of the slipping mechanism of the utility model in a slipping state;

[0037] Figure 9 It is an enlarged view of the butt joint surface between the locking part and the joint part when the utility model is in a slipping state;

[0038] Figure 10 yes Figure 4 An enlarged view of the first lug in the clutch disc shown;

[0039] Figure 11 It is an enlarged view of the contact surface between the cantilever and the sliding part in the utility model;

[0040] Figure 12 It is a stereogram of the delivery system of the utility model.

[0041] In the figure, 1, driving gear, 2, clutch plate, 3, clutch gear, 4, cantilever, 401, first abutting surface, 402, transition surface, 403, ramp surface, 5, first sleeve, 6, first protrusion, 601, clutch part, 602, locking part, 603, sliding part, 604, limiting surface, 605, first end face, 606, second abutting surface, 607, radial protrusion, 7, second protrusion, 701, joint part, 702, abutting part, 8, protrusion A, 9, protrusion B, 10, second sleeve, 11, driving motor, 12, sliding mechanism. DETAILED DESCRIPTION

[0042] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0043] The present utility model provides a slipping mechanism, which includes a clutch disc 2 and a clutch gear 3. The clutch disc 2 and the clutch gear 3 are coaxially arranged separately. The clutch disc 2 is a connecting member between the clutch gear 3 and the driving gear 1, which plays a role in connecting or separating the two. At least one first protrusion 6 is fixed on the clutch disc 2. The thicknesses of the two circumferential ends of the first protrusion 6 are unequal. A second protrusion 7 is fixed on the clutch gear 3. The first protrusion 6 and the second protrusion 7 are arranged in a crossed and spaced manner. The shapes of the two circumferential ends of the first protrusion 6 are respectively adapted to the shapes of the two circumferential ends of the second protrusion 7. The clutch disc 2 rotates by a certain angle so that the two circumferential ends of the first protrusion 6 respectively and non-simultaneously abut against the two circumferential ends of the second protrusion 7. That is, when the slipping mechanism 12 is in the first state, one end of the first protrusion 6 abuts against one end of the second protrusion 7. After the clutch disc 2 rotates by a certain angle relative to the clutch gear 3, the slipping mechanism 12 reaches the second state. At this time, the other end of the first protrusion 6 abuts against the other end of the second protrusion 7.

[0044] The present utility model adds a clutch disc 2 to the traditional slipping mechanism 12. The thicknesses of the two ends of the first protrusion 6 in the clutch disc 2 are unequal. The thicker end abuts against the driving gear 1 in the locked state. Then, in the locked state, the thinner end abuts against the second protrusion 7. When the slipping mechanism 12 reaches the slipping state, the driving gear 1 will disengage from the end face of the first protrusion 6. At this time, the thicker end of the first protrusion 6 abuts against the end of the second protrusion 7, thereby eliminating this end face. When the driving gear 1 passes through the thicker end of the first protrusion 6 during the slipping process, it can directly slide to the second protrusion 7, and there is no radial mutation.

[0045] The driving gear 1 can cooperate with the clutch disc 2 through a leaf spring or a protrusion made of deformable material to realize the switching between the slipping and locked states. The present utility model preferably adopts a cantilever 4 type structure, that is, one end of the driving gear 1 is fixed with a cantilever 4, and a first abutting surface 401 is formed at the end of the cantilever 4; the first abutting surface 401 abuts against one end face of the first protrusion 6 when the slipping mechanism 12 is in the locked state, and the thickness of this end face is greater than the thickness of the other end of the first protrusion 6. A slipping part 603 for radially pressing the cantilever 4 is provided in the middle of the first protrusion 6, so that the cantilever 4 can drive the clutch disc 2 to rotate by a certain angle.

[0046] Embodiment 1

[0047] As Figures 1 - 5 shown, a slipping mechanism 12 includes a driving gear 1, a clutch disc 2 and a clutch gear 3, which are coaxially arranged in sequence. The driving gear 1 is meshed with a driving component for transmission, and the clutch gear 3 is meshed with a working component for transmission. The clutch disc 2 connects the driving gear 1 and the clutch gear 3 when the slipping mechanism 12 is in the locked state. At this time, the clutch gear 3 and the driving gear 1 rotate synchronously; the clutch disc 2 separates the driving gear 1 and the clutch gear 3 when the slipping mechanism 12 is in the slipping state, and the driving gear 1 rotates independently.

[0048] The driving gear 1 of the present utility model adopts a conventional cantilever 4 type structure, that is, a cantilever 4 is fixed at one axial end of the driving gear 1, and a first abutting surface 401 is formed at one end of the cantilever 4. As Figure 2 shown, a first bushing 5 is provided at the center of the driving gear 1. One end of the first bushing 5 protrudes from the end face of the driving gear 1. One end of the cantilever 4 is fixed on the first bushing 5, and the other end is a free end. The first abutting surface 401 is located at the end face of the free end. The design with one end suspended enables the cantilever 4 to deform radially.

[0049] The clutch disc 2 is located between the driving gear 1 and the clutch gear 3. The clutch disc 2 is provided with a clutch part 601, a locking part 602, and a slipping part 603 connecting the clutch part 601 and the locking part 602; the clutch gear 3 is provided with a engaging part 701 and an abutting part 702. The locking part 602 cooperates with the first abutting surface 401 of the cantilever 4 or with the engaging part 701 in different states. The clutch part 601 is used to cooperate with the abutting part 702, and the slipping part 603 is used to squeeze the cantilever 4 so that the clutch disc 2 can rotate a certain angle and then cooperate with the engaging part 701 before the mechanism is ready to enter the slipping state.

[0050] When the driving gear 1 rotates in the first direction, the first abutting surface 401, the locking part 602, and the engaging part 701 can abut in sequence along the rotation direction. At this time, the slipping mechanism 12 is in the locked state, and the driving gear 1 drives the clutch gear 3 to rotate through the clutch disc 2; when the driving gear 1 rotates in the reverse direction of the first direction (the first direction can be counterclockwise or clockwise), the cantilever 4 and the slipping part 603 are squeezed and rubbed to drive the clutch disc 2 to rotate until the locking part 602 of the clutch disc 2 cooperates and docks with the engaging part 701 of the clutch gear 3. The first abutting surface 401 of the cantilever 4 is in end face abutment with the locking part 602 in the free state, and the cantilever 4 and the slipping part 603 are in lateral squeezing and rubbing. Therefore, in the radial direction, the contact surface between the slipping part 603 and the cantilever 4 is located inside the contact surface between the locking part 602 and the cantilever 4. When there is no relative movement between the clutch disc 2 and the clutch gear 3, the cantilever 4 will produce a radial mutation when passing through the locking part 602 from the direction of the slipping part 603, thereby generating noise and reducing the service life of the cantilever 4.

[0051] In the present utility model, the squeezing frictional force between the cantilever 4 and the slipping part 603 can drive the clutch disc 2 to rotate, so that the clutch disc 2 can rotate relative to the clutch gear 3 by a certain angle until the locking part 602 of the clutch disc 2 is in mating connection with the engaging part 701 of the clutch gear 3. The said mating connection means that the two end faces just engage with each other, enabling the locking part 602 and the engaging part 701 to have a smooth transition, eliminating the end face of the locking part 602 and eliminating the mutation. The clutch disc 2 and the clutch gear 3 are in end face docking between the locking part 602 and the engaging part 701, while the driving gear 1 and the clutch disc 2 are in side friction contact between the cantilever 4 and the slipping part 603. The driving gear 1 with side friction can only drive the clutch disc 2 to move alone and cannot support the rotation of the clutch gear 3 or even the working components. Therefore, after the locking part 602 of the clutch disc 2 is in mating connection with the engaging part 701 of the clutch gear 3, the cantilever 4 will slip with the slipping part 603 and directly enter the engaging part 701 after passing through the locking part 602, without a mutation step. Thus, the cantilever 4 smoothly transitions through the locking part 602. At this time, when the slipping mechanism 12 is in a slipping state, the driving gear 1 cannot drive the clutch gear 3 to rotate.

[0052] The clutch part 601, the locking part 602, and the slipping part 603 can be respectively arranged on the clutch disc 2, as long as the slipping part 603 is connected to the clutch part 601 and the locking part 602. Or the clutch part 601, the locking part 602, and the slipping part 603 can be hollow bodies with corresponding working surfaces. For the convenience of processing, the present utility model preferably integrally forms the clutch part 601, the locking part 602, and the slipping part 603 into a first convex block 6, as Figure 1 and Figure 4 shown. The first convex block 6 is fixed on the clutch disc 2. The clutch part 601 and the locking part 602 are located at the circumferential two ends of the first convex block 6, and the slipping part 603 is located in the middle of the first convex block 6. The radial inner side of the slipping part 603 is in squeezing friction with the cantilever 4. The first convex block 6 and the cantilever 4 can be equal or unequal.

[0053] The engaging part 701 and the abutting part 702 can also be respectively arranged on the clutch gear 3. The arrangement requirement is that the engaging part 701 and the abutting part 702 need to be arranged crosswise. After the driving gear 1, the clutch disc 2, and the clutch gear 3 are assembled, the engaging part 701 and the abutting part 702 are respectively on both sides of each first convex block 6. Only in this way can it be ensured that before and after the relative rotation of the clutch disc 2 and the clutch gear 3, the locking part 602 of the first convex block 6 can be in end face mating with the engaging part 701, and the clutch part 601 of the first convex block 6 can be in end face mating with the abutting part 702. Similar to the design of the first convex block 6, the present utility model preferably integrally forms the engaging part 701 and the abutting part 702 and forms a second convex block 7, as Figure 1 and Figure 5As shown, the second bump 7 is fixed to one end of the clutch gear 3 and corresponds to the first bump 6 one by one. The joint portion 701 and the abutting portion 702 are located at the circumferential two ends of the second bump 7. After the clutch disc 2 and the clutch gear 3 are assembled, the first bump 6 and the second bump 7 need to be arranged crosswise in the circumferential direction, and the orientations of the same parts on each first bump 6 and each second bump 7 are the same, ensuring that the engaging portion 601 and the abutting portion 702 are opposite in the circumferential direction, and the locking portion 602 and the joint portion 701 are opposite. Since the end of the second bump 7 does not need to abut against the first abutting surface 401 of the cantilever 4, after the cantilever 4 passes over the locking portion 602 and enters the joint portion 701, the deformation of the cantilever 4 can be gradually reduced through the transition of the inner side surface of the second bump 7, thereby avoiding the radial mutation of the cantilever 4. Preferably, the inner side surface of the second bump 7 is an inclined surface that transitions and connects the joint portion 701 and the abutting portion 702. This inclined surface can be an arc surface or a joint of multiple planes, as long as it can gradually relax the cantilever 4 from the joint portion 701 to the abutting portion 702.

[0054] In the present utility model, a clutch disc 2 is added to the traditional slipping mechanism 12. As Figure 1 and Figure 4 shown, when rotating in the counterclockwise direction in Figure 6 , the cantilever 4 is combined with the locking portion 602 on the clutch disc 2, and the engaging portion 601 of the clutch disc 2 drives the clutch gear 3 to rotate. At this time, the slipping mechanism 12 is in the locked state; when rotating in reverse, the cantilever 4 drives the clutch disc 2 to rotate through a certain angle. At this time, the locking portion 602 of the clutch disc 2 will be combined with the joint portion 701 of the clutch gear 3 (as Figure 8 shown), enabling the cantilever 4 to slip smoothly. The slipping mechanism 12 is in the slipping state without any sudden deformation, thereby greatly improving the service life of the slipping mechanism 12 and significantly reducing the noise of the slipping mechanism 12.

[0055] For convenience of description, in this article, the rotation of the driving gear 1 when the slipping mechanism 12 is in the locked state is defined as forward rotation, and the rotation of the driving gear 1 when the slipping mechanism 12 is in the slipping state is defined as reverse rotation.

[0056] If the number of the first bumps 6 is too large, it will cause the cantilever 4 to be squeezed for a long time, the friction frequency of the cantilever 4 is high, and the wear increases. If the number of the cantilever 4, the first bumps 6 and the second bumps 7 is too small, it may cause insufficient frictional force and be unable to support the reverse rotation of the clutch disc 2. Therefore, it is preferred that three cantilevers 4, the first bumps 6 and the second bumps 7 are all arranged in an array. At this time, not only can the clutch disc 2 be driven to rotate in the reverse direction by a certain angle, but also the cantilever 4 can be in a free state for a long time during the slipping process, reducing the friction frequency between the cantilever 4 and the slipping portion 603 and improving the reliability of the slipping mechanism 12.

[0057] As Figure 1As shown in the figure, in this embodiment, the first bump 6 protrudes from the surface of the clutch disc 2 towards the driving gear 1. A second sleeve 10 is provided at the center of the clutch gear 3. Both the second sleeve 10 and the second bump 7 protrude towards the clutch disc 2. The clutch disc 2 is sleeved outside the second sleeve 10, so that the first bump 6 of the clutch disc 2 and the second bump 7 of the clutch gear 3 are located on the same plane.

[0058] Since the slipping part 603 on the first bump 6 needs to squeeze the cantilever 4 to drive the clutch disc 2 to rotate a certain angle, the inner diameter of the slipping part 603 is relatively small. There is no direct relationship between the second bump 7 and the cantilever 4. It is only used to cooperate with the end face of the first bump 6. In order to minimize the friction between the cantilever 4 and the second bump 7 during slipping, the inner diameter of the second bump 7 should be increased as much as possible. Preferably, the minimum inner diameter of the second bump 7 is greater than the minimum inner diameter of the first bump 6.

[0059] Embodiment Two

[0060] On the basis of Embodiment One, the circumferential end face of the locking part 602 is a stepped end face that gradually protrudes circumferentially from the inside to the outside. When the slipping mechanism 12 is in the locked state, the first abutting surface 401 abuts against the end face of the locking part 602 close to the inside, and the locking part 602 has a limiting surface 604 that shields the outside of the cantilever 4. The stepped end face has at least two layers of stepped structures. The stepped design of the end face is to have a limiting surface 604 that shields the outside of the cantilever 4 when the first abutting surface 401 abuts against the locking part 602, to prevent the cantilever 4 from radially deforming and sliding out of the locking part 602 when it is subjected to rotational resistance.

[0061] Since only two layers of stepped structures are needed for the stepped end face to form the limiting surface 604, in order to minimize the circumferential angle occupied by the first bump 6 and increase the free state time of the cantilever 4, preferably the stepped end face is a two-layer stepped structure, that is, it includes a first end face 605 and a second abutting surface 606. As Figure 4 shown, the second abutting surface 606 is located radially inside the first end face 605 and is retracted circumferentially towards the clutch part 601, so as to form a limiting surface 604 inside the first end face 605. When the cantilever 4 abuts against the second abutting surface 606, the limiting surface 604 is located outside the cantilever 4 to shield the cantilever 4 and prevent the cantilever 4 from radially expanding and disengaging from the second abutting surface 606.

[0062] Embodiment Three

[0063] On the basis of Embodiment Two, in order to prevent the cantilever 4 from deforming under pressure and disengaging from the inside of the second abutting surface 606, in this embodiment, it is preferably that the second abutting surface 606 is arranged radially inclined with respect to the clutch gear 3, so that an acute angle is formed between the second abutting surface 606 and the tangent of the limiting surface 604. As Figure 10As shown, at this time, the side of the second abutting surface 606 facing the limiting surface 604 is recessed inward. As Figure 3 , Figure 4 and Figure 6 shown, when the driving gear 1 rotates counterclockwise, the first abutting surface 401 of the cantilever 4 engages with the locking portion 602 of the clutch gear 3, driving the clutch gear 3 to rotate. At the same time, since the second abutting surface 606 is inclined at a certain angle, during the locking process of the cantilever 4, the first abutting surface 401 slides radially outward along the second abutting surface 606 by a certain amount, increasing the force-bearing structure between the cantilever 4 and the locking portion 602 and making the locking more reliable. At the same time, the inclined angle of the second abutting surface 606 can prevent the cantilever 4 from sliding inward, causing the slipping mechanism 12 to fail, and also gives a certain buffer to the cantilever 4 to prevent excessive impact from causing permanent deformation of the cantilever 4.

[0064] Correspondingly, in order to make the first abutting surface 401 fit the second abutting surface 606 as much as possible, the first abutting surface 401 is also inclined relative to the radial direction of the driving gear 1, and the inclination direction of the first abutting surface 401 is opposite to that of the second abutting surface 606.

[0065] Let the inclination angle of the first abutting surface 401 be α, and the inclination angle of the second abutting surface 606 relative to the radial direction of the clutch gear 3 be β. If α < β, it is not easy for the first abutting surface 401 to slide radially outward along the second abutting surface 606, and the abutting effect between the two is reduced. Therefore, it is preferably α ≥ β, so that after the cantilever 4 deforms radially outward to a stable state during locking, the included angle between the first abutting surface 401 and the second abutting surface 606 is very small or they are directly in contact, which not only increases the contact area but also reduces the wear of the sharp parts.

[0066] The respective inclination angles of the first abutting surface 401 and the second abutting surface 606 also affect the abutting effect. Excessive inclination angles are not conducive to the machining of the end face and are also prone to cause the fracture of the sharp parts. Therefore, preferably, 0 < α < 60 and 0 < β < 60. In this embodiment, β = 10° and α = 15°. When β is 10°, it can make the locking of the cantilever 4 more reliable, and when α is 15° (greater than 10° of β), the first abutting surface 401 of the cantilever 4 slides on the second abutting surface 606 of the clutch disc 2, making the cantilever 4 fully abut against the locking portion 602. At the same time, this small deformation just makes the first abutting surface 401 and the second abutting surface 606 coincide, making the locking more reliable.

[0067] Embodiment 4

[0068] On the basis of the above embodiment, in this embodiment, the contact surface between the slipping portion 603 and the cantilever 4 is designed to ensure that the frictional force between the cantilever 4 and the slipping portion 603 during reverse rotation is sufficient to drive the rotation of the clutch portion 601.

[0069] The slipping part 603 has a radial protrusion 607 that radially presses the cantilever 4, and the radial protrusion 607 is arranged closer to the clutch part 601. As Figures 6 - 8 shown, taking one of the cantilevers 4 as an example to describe its motion state, the relevant first bumps 6 that cooperate with it are respectively named bump A8 and bump B9. Then in Figure 6 , this cantilever 4 abuts against the locking part 602 of the bump A8. When the driving gear 1 rotates counterclockwise from the Figure 6 shown locked state, this cantilever 4 first passes through the second bump 7 between the bump A8 and the bump B9 and then reaches the bump B9. The radial protrusion 607 inside the bump B9 squeezes the cantilever 4. The setting of the radial protrusion 607 can increase the squeezing force on the cantilever 4, enabling the cantilever 4 to drive the clutch disc 2 to rotate to the Figure 8 shown state. At this time, the bump B9 abuts against the second bump 7 in front of its rotation direction. The other surfaces of the slipping part 603 except the radial protrusion 607 have a smaller squeezing force on the cantilever 4. Therefore, during the slipping state, when the cantilever 4 rotates, only at the radial protrusion 607 will it be subjected to a large squeezing force, with less deformation time. The radial protrusion 607 and the other surfaces of the slipping part 603 can have a smooth transition, and the cantilever 4 will not have a radial mutation.

[0070] When the cantilever 4 suddenly rotates forward after slipping past the radial protrusion 607, the setting of the radial protrusion 607 will impose a certain hindrance on the forward rotation of the cantilever 4. Therefore, it is necessary to optimize the design of the end of the cantilever 4. As Figure 11 shown, the outer side of the free end of the cantilever 4 has an inwardly converging transition surface 402, and the transition surface 402 can pass through either side of the radial protrusion 607. When the cantilever 4 moves from the Figure 11 right side of the radial protrusion 607 to the left side in the figure, the inclination direction of the transition surface 402 is the same as that of the right slope surface of the radial protrusion 607, which helps the cantilever 4 cross the right slope surface of the radial protrusion 607.

[0071] Furthermore, in this embodiment, corresponding designs are made for the outer side surface of the cantilever 4 in the case where the radial protrusion 607 is provided. Specifically, it means that: the outer side of the cantilever 4 has a slope surface 403 connected to the transition surface 402, and the slope surface 403 gradually extends radially outward from the side far from the free end of the cantilever 4 to the side close to the free end of the cantilever 4. As Figure 11 shown, at the contact position between the front end of the cantilever 4 and the clutch disc 2, there is a slope surface 403. When it rotates to the position of the radial protrusion 607, the slope surface 403 contacts and fits with the radial protrusion 607, driving the clutch disc 2 to move. In addition, there is a certain frictional force between the cantilever 4 and the radial protrusion 607, which can assist the cantilever 4 to drive the clutch disc 2 to rotate. In this scheme, the cantilever 4 has almost no impact on the clutch disc 2, which can effectively reduce noise and also extend the service life of the structure of the cantilever 4.

[0072] Embodiment Five

[0073] In the above embodiments, in the slipping state, the inner diameters of the mating surfaces of the locking portion 602 and the engaging portion 701 will affect the running noise of the whole machine. If the inner diameter of the engaging portion 701 at the docking surface between the engaging portion 701 and the locking portion 602 is greater than the inner diameter of the locking portion 602 at this location, then the inner side of the clutch disc 2 protrudes beyond the inner side of the clutch gear 3 at the docking surface, and the cantilever 4 suddenly changes from the compressed state to the relaxed state, which may impact the clutch gear 3 and generate noise.

[0074] Therefore, on the basis of the above embodiments, the following improvements are made in this embodiment. When the engaging portion 701 and the locking portion 602 are in mating connection, the inner diameter of the engaging portion 701 at the docking surface between the engaging portion 701 and the locking portion 602 is smaller than the inner diameter of the locking portion 602 at this location, and is greater than the minimum inner diameter of the slipping portion 603 (as Figure 9 shown). When the cantilever 4 rotates from the locking portion 602 of the clutch disc 2 to the engaging portion 701 of the clutch gear 3, the cantilever 4 changes from a relatively relaxed state to a compressed state. From relaxation to tension, the cantilever 4 will not impact the clutch gear 3 or the clutch disc 2 to generate noise. This design is mainly to prevent the height difference at the docking surface from not meeting the requirements due to machining errors.

[0075] Embodiment Six

[0076] After the driving gear 1 and the clutch disc 2 are assembled, the slipping portion 603 on the clutch disc 2 will press the cantilever 4 on the driving gear 1. During machining, the slipping portion 603 protrudes inward with the arc where the limiting surface 604 is located as the reference. If the protruding height of the slipping portion 603 is too large, it is easy to cause excessive deformation of the cantilever 4, which may lead to permanent deformation. At the same time, an appropriate protruding height can not only reduce the deformation, but also make the slipping force smaller when slipping. When the slipping process is too fast, no significant noise will be generated.

[0077] Therefore, in this embodiment, the protruding height of the slipping portion 603 is limited. Specifically, as Figure 11 shown, the radial distance between the arc surface where the limiting surface 604 is located and the radial inner side of the first convex block 6 is X, then 0 < X < 1 mm. This distance limit mainly applies to the transition area of the slipping portion 603. When the slipping portion 603 is provided with a radial protrusion 607, since the area of the radial protrusion 607 is small and the deformation time of the cantilever 4 caused is short, the value of X here can be greater than 1 mm. That is, the value of X represents the protruding height of the slipping portion 603 between the radial protrusion 607 and the second abutting surface 606 in the figure. In this embodiment, X = 0.7 mm. At this distance, the deformation of the cantilever 4 is small, the slipping force is also small, and no significant noise will be generated during the slipping process.

[0078] Embodiment Seven

[0079] A liquid adding pump, the liquid adding pump includes a driving motor 11 and one or more than two of the slipping mechanisms 12 connected to the driving motor 11, and the driving gear 1 of the slipping mechanism 12 meshes and drives with the output end of the driving motor 11.

[0080] When the slipping mechanism 12 is locked, the cantilever 4 drives the clutch disc 2, and the clutch disc 2 drives the clutch gear 3, and the liquid adding pump can work; when the mechanism slips, the cantilever 4 cannot drive the clutch disc 2, and the liquid adding pump does not work.

[0081] The driving motor 11 can be connected to only one slipping mechanism 12 to meet the start or stop of the working components in the state where the driving motor 11 does not stop working.

[0082] In common scenarios, the driving motor 11 is connected to two slipping mechanisms 12 to form a two-station pump. For example, in the dosing systems of household appliances such as dishwashers or washing machines, there are usually two dosing chambers, which respectively contain two kinds of detergents. The two detergents are not dosed at the same time. The two slipping mechanisms 12 are respectively placed in the two chambers, and the driving gears 1 of the two slipping mechanisms 12 are simultaneously meshed with the output end of the driving motor 11. When the driving motor 11 rotates forward, one of the slipping mechanisms 12 is in the locked state to dose the detergent in this chamber, and the other slipping mechanism 12 is in the slipping state. When the driving motor 11 rotates in reverse, the two slipping mechanisms 12 switch states.

[0083] The driving gear 1 can be a spur gear. At this time, a spur gear is also correspondingly provided on the output shaft of the driving motor 11 that meshes with it. Usually, in the slipping mechanism 12 of the dosing system, the driving gear 1 is a helical gear, and a helical gear is correspondingly provided on the output shaft of the driving motor 11 that meshes with it.

[0084] Such as Figure 12 As shown, the helical gear is installed on one side of the driving motor 11 of the DC double pump. When the driving motor 11 starts, the pump chamber on one side works normally, and the pump chamber on the other side does not work due to the slipping of the slipping mechanism 12. In this way, by controlling the forward and reverse rotation of the driving motor 11, the work of the two pump chambers can be orderly controlled.

[0085] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "left", "right", "inner", "outer", "axial", "radial", "circumferential", etc. is the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0086] In addition, the terms "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0087] In this specification, the schematic description of the terms does not necessarily refer to the same embodiment. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments in a suitable manner.

[0088] Based on the above enlightenment of the ideal embodiment of the present utility model, through the above description, relevant staff can completely make various changes and modifications without departing from the technical idea of the present utility model. The technical scope of the present utility model is not limited to the content in the specification, and its technical scope must be determined according to the scope of the claims.

Claims

1. A slipping mechanism, characterized in that: It includes a clutch disc and a clutch gear. At least one first protrusion is fixed on the clutch disc. The thicknesses of the two circumferential ends of the first protrusion are unequal. A second protrusion is fixed on the clutch gear. The first protrusions and the second protrusions are arranged in a crossed and spaced manner. The two circumferential ends of the first protrusion are respectively adapted to the two circumferential ends of the second protrusion in shape. The clutch disc rotates by a certain angle so that the two circumferential ends of the first protrusion respectively and non-simultaneously abut against the two circumferential ends of the second protrusion.

2. The slip mechanism according to claim 1, characterized in that: The slipping mechanism further includes a driving gear. One end of the driving gear is fixed with a cantilever, and the end of the cantilever forms a first abutting surface. When the slipping mechanism is in the locked state, the first abutting surface abuts against one end face of the first protrusion, and the thickness of this end face is greater than the thickness of the other end of the first protrusion. A slipping part for radially pressing the cantilever is provided in the middle of the first protrusion, so that the cantilever can drive the clutch disc to rotate by a certain angle.

3. The slip mechanism according to claim 2, wherein: The two circumferential ends of the first protrusion are respectively a clutch part and a locking part, and the two circumferential ends of the second protrusion are respectively a coupling part and an abutting part. The clutch part is opposite to the abutting part, and the locking part is opposite to the coupling part. When the slipping mechanism is in the locked state, the first abutting surface abuts against the end face of the locking part. When the driving gear rotates in the first direction, the first abutting surface, the locking part and the coupling part can abut in sequence. At this time, the slipping mechanism is in the locked state, and the driving gear drives the clutch gear to rotate through the clutch disc. When the driving gear rotates in the reverse direction of the first direction, the cantilever and the slipping part are squeezed and rubbed to drive the clutch disc to rotate until the locking part of the clutch disc is cooperatively butted with the coupling part of the clutch gear, so that the cantilever smoothly transitions through the locking part. At this time, the slipping mechanism is in the slipping state, and the driving gear cannot drive the clutch gear to rotate.

4. The slip mechanism according to claim 3, characterized in that: The circumferential end face of the locking part is a stepped end face that gradually protrudes circumferentially from the inside to the outside. When the slipping mechanism is in the locked state, the first abutting surface abuts against the end face close to the inside of the locking part, and the locking part has a limiting surface that shields the outside of the cantilever.

5. The slipping mechanism according to claim 4, wherein: Let the end face of the locking part that abuts against the first abutting surface be the second abutting surface. The second abutting surface is arranged obliquely with respect to the radius of the clutch gear, so that an acute angle is formed between the second abutting surface and the tangent of the limiting surface.

6. The slip mechanism according to claim 5, characterized in that: The first abutting surface is arranged obliquely with respect to the radius of the driving gear, and the inclination angle is α. The inclination angle of the second abutting surface with respect to the radius of the clutch gear is β, then β ≤ α.

7. The slip mechanism according to claim 6, characterized in that: 0＜α＜60，0＜β＜60。 8. The slip mechanism according to claim 7, wherein: β=10°，α=15°。 9. The slip mechanism according to claim 1, characterized in that: The minimum inner diameter of the second protrusion is greater than the minimum inner diameter of the first protrusion.

10. The slip mechanism according to claim 2, characterized in that: The slipping part has a radial protrusion for radially pressing the cantilever.

11. The slip mechanism according to claim 10, characterized in that: The outer side of the free end of the cantilever has an inwardly retracted transition surface, and the transition surface can pass through either side of the radial protrusion.

12. The slip mechanism according to claim 11, wherein: The outer side of the cantilever has a ramp surface connected to the transition surface. The ramp surface gradually extends radially outward from the side far from the free end of the cantilever to the side close to the free end of the cantilever.

13. The slip mechanism according to claim 3, wherein: When the coupling part and the locking part are cooperatively butted, the inner diameter of the coupling part at the butting surface of the coupling part and the locking part is smaller than the inner diameter of the locking part at this position and greater than the minimum inner diameter of the slipping part.

14. The slip mechanism according to claim 3, wherein: The inner side surface of the second protrusion is an inclined surface for transitionally connecting the coupling part and the abutting part.

15. The slip mechanism according to claim 4, characterized in that: The radial distance between the arc surface where the limiting surface is located and the radial inside of the first protrusion is X, then 0 < X < 1 mm.

16. The slip mechanism according to claim 15, characterized in that: X = 0.7 mm.

17. The slip mechanism according to any one of claims 2-16, characterized in that: The first bump protrudes from the surface of the clutch disc towards the driving gear.

18. A liquid adding pump, characterized in that: The liquid adding pump includes a driving motor and one or two slip mechanisms according to any one of claims 1-17 connected to the driving motor, and the driving gear of the slip mechanism is in meshing transmission with the output end of the driving motor.

19. A delivery system, characterized in that: It includes the liquid adding pump according to claim 18.

20. A household appliance, characterized in that: It includes the feeding system according to claim 19.

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