Double distributor

Abstract

A dual dispenser comprising two pumps (P1, P2), i.e.: a first pump (P1) provided with a first actuation pin (P11) axially displaceable within a first maximum stroke; and-a second pump (P2) provided with a second actuating pin (P21) axially displaceable within a second maximum stroke, the distributor comprising an axially displaceable common piston (B) acting axially and directly on the first actuating pin (P11) in order to drive the first actuating pin within its first maximum stroke, and-a second pump (P2) provided with a second actuating pin (P21) axially displaceable within a second maximum stroke, the distributor comprising an axially displaceable common piston (B) acting axially and directly on the first actuating pin (P11) in order to drive the second actuating pin within its second maximum stroke. Characterized in that:-the first maximum stroke is greater than the second maximum stroke, and-the distributor further comprises gearing-down means (1) acting between the common piston (B) and the second actuating pin (P21) in order to transmit the axial thrust of the common piston (B) to the second actuating pin (P21) wherein the speed of the second actuating pin (P21) is reduced relative to the speed of the first actuating pin (P11).

Description

[0001] The invention relates to a double dispenser comprising two pumps, namely: a first pump provided with a first actuating pin which can be axially displaced within a first maximum stroke; and a second pump provided with a second actuating pin which can be axially displaced within a second defined maximum stroke. The dispenser also comprises a common piston which can be axially displaced and acts axially and directly on the first actuating pin so as to drive the first actuating pin within its first maximum stroke.

[0002] In the prior art, there are already dual dispensers in which the dose can be adjusted by adjusting the stroke of the actuating pin; by limiting the stroke of the actuating pin, only a partial dose is dispensed. Thus, the ratio of the two doses delivered can be changed. This is not the purpose of the present invention.

[0003] In the prior art, there are already double distributors with different pin strokes, one larger than the other. A catch-up or compensation system is then provided for the shortest stroke, which usually includes a sliding or telescopic sealed connection. Both strokes are performed at the same speed, but with a delay or early end for the shortest stroke. This is not the purpose of the present invention.

[0004] In the prior art, there are also double distributors using a common pivoting or rotating piston, such as the double distributor in document WO2019 / 208335 A1. The requirement of the present invention is that the common piston is only displaced axially without a pivoting or rotating part.

[0005] The main purpose of the invention is to change the speed of the actuating pin with the shortest stroke with a general decreasing trend relative to the speed of the other actuating pin with a longer stroke using a common piston that is only axially displaced. The purpose is not to reduce one dose relative to the other, nor to compensate for the difference in stroke caused by the initial or final dead stroke, but to drive the two pins at different speeds.

[0006] In order to overcome this technical problem, which is itself inventive, the present invention proposes a double dispenser comprising two pumps, namely:

[0007] a first pump provided with a first actuating pin which is axially displaceable within a first maximum stroke, and

[0008] a second pump provided with a second actuating pin which is axially displaceable within a second maximum stroke,

[0009] The distributor comprises a common piston which is axially displaceable and acts axially and directly on the first actuating pin in order to drive the first actuating pin within a first maximum stroke of the first actuating pin,

[0010] Features:

[0011] - the first maximum stroke is greater than the second maximum stroke, and

[0012] The distributor further comprises reduction transmission means acting between the common piston and the second actuating pin in order to transmit the axial thrust of the common piston to the second actuating pin, wherein the speed of the second actuating pin is reduced relative to the speed of the first actuating pin.

[0013] These reduction transmissions can also be described more simply as speed reducers for the speed of one pin relative to the other pin. In other words, these reduction transmissions allow the two actuating pins to be displaced simultaneously, but at different non-zero speeds. As an example, over the full travel of the two pins, a pin having a travel corresponding to half the travel of the other pin will be able to displace at half the speed of the other pin.

[0014] This reducer is already inventive in terms of the technical problem of simultaneously actuating two actuating pins with different strokes with a common piston. Rather than the following problem: actuating both pins simultaneously at the same speed until the end of the shortest stroke and then stopping the longest stroke. This has been fully explained above.

[0015] Documents US2016 / 361732 A1 and JP 4686664 B2 disclose systems in which the speed of a pin that has completed its stroke is reduced relative to the speed of a pin that continues its stroke, since the speed of a pin that has completed its stroke is zero. This is not within the scope of our invention, since the main claim states that the speed is not zero.

[0016] Advantageously, the reduction transmission means comprises an actuating cam in contact with the second actuating pin so as to displace the second actuating pin within its second maximum stroke, the actuating cam comprising a contact surface in dynamic contact with the second actuating pin, the contact surface having a profile that influences the displacement speed of the second actuating pin. An actuating cam with a regular or linear profile will produce a speed V2 of actuating pin displacement that is proportional to the speed V1 of the other actuating pin displacement. It can then be said that V2=K×V1, where K is a constant less than 1. Conversely, an actuating cam with an irregular or complex profile will produce a speed V2 of actuating pin displacement that is not proportional to the speed V1 of the other actuating pin displacement. It can then be said that V2=f(p)×V1, where p is the slope of the contact surface and where f(p) varies between 0 and 1. It is not excluded that f(p) is locally constant, i.e. has a regular or linear profile. Many combinations are possible, combining continuous speed stages that may be proportional and variable. By way of example, it is possible to envisage four different phases for V2, during which V1 is constant: a first phase, in which V2=0; a second phase, in which V2=V1; a third phase, in which V2=f(p)×V1; and a fourth phase, in which V2=K×V1. In this explicit case, the reduction transmission device intervenes only in the second, third and fourth phases, the first phase being the dead stroke of the second actuating pin.

[0017] It can be clearly seen that the reduction transmission means do not prohibit them from being associated with dose adjustment or stroke catch-up means: it should be noted that the reduction transmission means act during the stroke of the two pins, not before the stroke of the two pins or after the stroke of the two pins.

[0018] Due to the reduction transmission means, the first maximum stroke and the second maximum stroke can be performed completely and simultaneously by axially pushing the common piston.The speeds of the two actuating pins can be proportional and / or variable.

[0019] According to a first embodiment, the reduction transmission means comprises a movable element which turns about a vertical axis of rotation fastened to a common piston.

[0020] Advantageously, the movable element comprises:

[0021] - shaft housing for the vertical axis of rotation of the common piston,

[0022] - a rotary drive member which is in sliding contact on a fixed curved inclined ramp, and

[0023] - an actuating cam which is in sliding contact with the second actuating pin.

[0024] Preferably, the actuating cam comprises a contact surface engaging with the second actuating pin, the contact surface being at least partially inclined. However, the contact surface may also be partially planar. The planar profile and the inclined profile may follow each other.

[0025] According to another advantageous aspect of this first embodiment, the movable element can be made in one piece.

[0026] According to another feature of this first embodiment, the movable element can be biased in a rotational manner towards the starting position by a return spring, which is advantageously made in one piece with the movable element.

[0027] The advantage of this first embodiment lies in the fact that there is only a single movable part, i.e. a movable element, between the common piston and the fixed part of the distributor, which movable element can additionally be a single piece including a return spring. It is sufficient to form the common piston with a vertical axis of rotation, for example in the form of a small pin pointing downwards. As for the curved inclined ramp, it can be formed in the form of a truncated section of a cylinder at the fixed part of the distributor. Therefore, the movable element is the only component to be manufactured and installed between the common piston and the fixed part of the distributor, which makes this first embodiment particularly advantageous.

[0028] According to a second embodiment of the present invention, the reduction transmission device may include two hinged rods connected together at a common joint point, namely a first rod and a second rod, the first rod being hinged on a supporting part or a pivot part fastened to a common piston, and the second rod being hinged on a fixed supporting part or a pivot part, and the common joint point is provided with an actuating cam that contacts the second actuating pin.

[0029] Advantageously, the actuating cam may be connected to one of the two rods, preferably as a single piece.The actuating cam may have a regular and / or irregular profile in order to produce proportional and / or variable speed stages as described above.

[0030] According to a third embodiment of the present invention, the reduction transmission device may include:

[0031] - a toothed wheel mounted on a fixed horizontal rotating shaft,

[0032] a toothed axial pin which is fastened to the common piston and which engages with the toothed wheel in order to drive the toothed wheel in rotation, and

[0033] - An actuating cam fastened to the toothed wheel and coming into contact with the second actuating pin.

[0034] Here too, the actuating cam may have a regular and / or irregular profile in order to produce proportional and / or variable speed stages as described above. The toothed axial pin may be made in one piece with the common piston, in the form of an elongated projection pointing downwards and provided with teeth on one of its two vertical edges. The fixed part of the dispenser may form two bearings for the horizontal axis of rotation of the toothed wheel.

[0035] In the three embodiments of the invention, although these three embodiments use very different components, the reduction transmission device interacts with the common piston and the fixed part of the distributor so as to displace the actuating cam while the common piston directly and axially pushes the first actuating pin, which pushes the second actuating pin. It should be remembered that the reduction transmission device only works when the first actuating pin is actuated by the common piston. Therefore, the second actuating pin is displaced simultaneously with the first actuating pin, but at an overall reduced speed, even though the two pins may be displaced instantaneously at the same speed within a limited stroke.

[0036] The invention will now be described in more detail below with reference to the accompanying drawings which show three embodiments of the invention by way of non-limiting examples.

[0037] In the attached picture:

[0038] Figure 1 is a perspective sectional view of the upper portion of the dispenser according to the first embodiment of the present invention in a stationary state,

[0039] Figure 2 is when the dispenser is in the actuated state Figure 1 A view similar to the view of

[0040] Figure 3 and Figure 4 yes Figure 1 A vertical cross-sectional view of the distributor in the vertical plane,

[0041] Figure 5 is a vertical sectional perspective view of a dispenser in a static state according to a second embodiment of the present invention,

[0042] Figure 6 The dispenser is in the actuated state and Figure 5 A view similar to the view of;

[0043] Figure 7 is a sectional perspective view of the upper part of the dispenser according to the second embodiment of the present invention in a static state,

[0044] Figure 8 is in the actuated state and Figure 7A view similar to that of

[0045] Fig. 9 It passes through Figure 7 Vertical cross-section of a distributor.

[0046] In three embodiments of the present invention, the dispenser includes common or similar components. First, the dispenser includes two pumps, P1 and P2, which are mounted on corresponding reservoirs (not shown). The detailed design of pumps P1 and P2 and reservoirs is not important for the present invention. It is simply necessary to know that pumps P1 and P2 are fixedly mounted on their corresponding reservoirs, and only the actuating pins P11 and P21 of pumps P1 and P2 can be axially displaced back and forth. This design is completely conventional for manual pumps in the fields of cosmetics, pharmacy or perfume. Actuating pins P11 and P21 return to the static position by a return spring, which can be as inside pump P1 or as outside pump P2. Reservoir, pumps P1 and P2 and all elements that allow the pump to be mounted on the reservoir together constitute the fixed part of the dispenser. Only actuating pins P11 and P21 can be displaced relative to this fixed part of the dispenser.

[0047] According to the invention, the pumps P1 and P2 are different relative to each other and more particularly the respective maximum axial strokes of the two actuating pins P11 and P21 are different. In the present case, the maximum axial stroke of the actuating pin P11 is greater than the maximum axial stroke of the actuating pin P21. It is therefore necessary to displace the actuating pin P11 by an axial distance greater than the axial distance displaced by the actuating pin P21 in order to dispense a full dose of the fluid product. It should be noted that when different pumps are used in a double dispenser, the maximum strokes of the two actuating pins of the two pumps are rarely the same.

[0048] The fundamental technical problem of the present invention is to actuate the two actuating pins P11 and P22 simultaneously, which requires that the displacement speed of the shortest actuating pin P21 relative to the longest actuating pin P11 be reduced. This technical problem is more obvious when the dispenser of the present invention includes a common piston that can be axially displaced along an axis parallel to the displacement axis of the two actuating pins P11 and P21. In other words, the common piston is only axially displaced without any rotating or pivoting parts. The common piston B is directly and axially connected to the actuating pin P11 through a connecting sleeve B11. On the other hand, the common piston B is connected to the actuating pin P21 through a sliding connecting sleeve B21. This means that the sleeve B21 can slide in a sealed manner inside the actuating pin P21. The connecting sleeve B11 is communicated with the distribution orifice B13 through a conduit B12. Similarly, the connecting sleeve B21 is communicated with another distribution orifice B23 through a conduit B22. Without departing from the scope of the present invention, sleeves B11 and B21 can also be communicated with a common dispenser orifice.

[0049] According to the invention, a reduction transmission device acts between the common piston and the actuating pin P21 so as to adjust the displacement speed of the actuating pin P21 relative to the displacement speed of the other actuating pin P11. In general, the reduction transmission device makes it possible to reduce the displacement speed of the actuating pin P21 relative to the displacement speed of the other actuating pin P11.

[0050] We will now refer more particularly to Figures 1 to 4 , in order to describe the reduction transmission device according to the first embodiment of the present invention. These reduction transmission devices include a movable element 1 of relatively complex design. The movable element 1 first includes a plate 11, which extends approximately horizontally, that is, perpendicularly to the displacement axis of the actuating pin and the displacement axis of the common piston B. The plate 11 rotates around a vertical or axial rotation axis B12 formed by the common piston B. In order to accommodate the rotation axis B12, the plate 11 forms an axis housing 12. The plate 11 is provided with a return spring 13, which enables the plate 11 to return to a static position. The return spring 13 acts between the plate 11 and the common piston B and can advantageously be made in one piece with the plate 11. On the other hand, the movable element 1 includes a rotary drive member 14, which is in sliding or gliding contact with a curved inclined ramp P14 formed by a fixed part of the dispenser. By way of example, the drive member 14 can be in the form of a pin extending downward from the lower surface of the plate 11. The free end of the pin 14 may be inclined so as to facilitate its sliding on the curved inclined ramp P14. The movable element 1 also comprises an actuating cam 15 extending laterally from the plate 11. This actuating cam 15 comprises a contact surface intended to bear on the actuating pin P21. The actuating cam 15 also comprises an upper bearing surface 153 on which the connecting sleeve B21 bears. More precisely, from Figure 3 As can be seen in FIG, the sleeve B21 terminates in a tube B211 which is sealingly and slidably engaged in the actuating pin P21. In other words, the actuating cam 15 is sandwiched between the connecting sleeve B21 and the actuating pin P21, thereby extending around the tube B211. Figure 1 and Figure 4 In the embodiment of the invention, it should be observed that the contact surface of the cam 15 comprises a plurality of sections, in particular a horizontal section 151 and an inclined section 152. This is here only a non-limiting embodiment and of course more sections, or on the contrary a single section, can be envisaged.

[0051] and Figure 3 and Figure 4 Same, in Figure 1, the common piston B is at rest: the actuating pins P11 and P21 are biased into the rest position by their respective return springs. Then, the movable element 1 is biased into the rest position of the movable element 1 by the spring 13. The drive member 14 is located at the top of the curved inclined ramp P14. The horizontal section 151 is in contact with the actuating pin P21.

[0052] By pushing the common piston B axially, the actuating pin P11 will be displaced. The same applies to the actuating pin P21, wherein the axial bearing force is transmitted by the connecting sleeve B21 and the actuating cam 15, and the horizontal section 151 of the actuating cam 15 is directly supported on the actuating pin P21. However, the axial displacement of the piston B also has the following effect: the movable element 1 is rotated around the axis B12 under the action of the actuating cam 14, and the actuating cam 14 slides on the curved inclined ramp P14. Therefore, the actuating cam 15 will be displaced horizontally, so that the inclined section 151 of the actuating cam 15 is in contact with the actuating pin P21. This Figure 2 . Since the segment 152 is inclined, the distance between the connecting sleeve B21 and the actuating pin P21 gradually decreases, which has the effect of reducing the displacement speed of the displacement pin P21 relative to the displacement speed of the other actuating pin P11. In this exemplary embodiment, the inclined segment 152 has a constant slope, so that the displacement speed of the actuating pin P21 is proportional or linear to the displacement speed of the actuating pin P11. This is another case if the inclined segment has a non-constant slope, for example convex or concave or actually corrugated.

[0053] In the present case where the actuating cam 15 has a horizontal section 151 and a constant inclined section 152, the actuating pin P21 is displaced in two different stages, namely an initial stage during which the displacement speed of the actuating pin P21 will be the same as the displacement speed of the actuating pin P11 (corresponding to the horizontal section 151) and a second stage during which the displacement speed of the actuating pin P21 is reduced relative to the displacement speed of the actuating pin P11, but with a constant ratio (corresponding to the inclined section 152). It will then be readily understood that by adjusting the configuration of the contact surfaces (151, 152) of the actuating cam 15, the displacement speed of the actuating pin P21 relative to the displacement speed of the other actuating pin P11 can be adjusted.

[0054] The rotation speed of the movable element 1 about the axis B12 can also be adjusted by adjusting the slope of the upper support surface 153 or the curved inclined ramp P14.

[0055] Now refer to Figure 5 and Figure 6, shows a double distributor of the invention in combination with a reduction transmission device 2 according to a second embodiment of the invention. The common piston B' may be similar to the common piston B of the first embodiment, except that the axis of rotation B12 has here been replaced by a first bearing B23 with a horizontal axis. At the fixed part of the distributor, the curved inclined ramp P14 has been replaced by a second bearing B24 with a horizontal axis. The two pumps P1 and P2 are identical to the two pumps P1 and P2 of the first embodiment.

[0056] The reduction transmission device 2 of this second embodiment comprises two rods 21 and 22 which are movable relative to each other while being connected by a common joint 20. The first rod 21 comprises an end 23 which rotates in an axle support B23. The second rod 22 comprises an end 24 which rotates in a second axle support B24. The second rod 22 is provided with an actuating cam 25 which forms a contact surface 251 which contacts an actuating pin P21, the maximum stroke of which is smaller than the maximum stroke of the other actuating pin P11. The contact surface 251 may be completely circular, or, on the contrary, the contact surface 251 may be contoured to contact the actuating pin P21. Figure 5 and Figure 6 The circular contact surface will cause a linear displacement of the actuating pin P21 relative to the other pin P11. Conversely, Figure 5 and Figure 6 The contoured contact surface 251 in the actuator causes a non-linear or non-proportional displacement relative to the pin P11. Therefore, here too, by adjusting the shape of the contact surface 251, the displacement speed of the actuating pin P21 can be adjusted relative to the displacement speed of the other actuating pin P11.

[0057] Now refer to Figures 7 to 9, shows another double dispenser of the invention in combination with a reduction transmission device 3 according to a third embodiment of the invention. The pump can be identical to the pumps of the first two embodiments of the invention. The common piston B" can have a similar design, except for the rotation axis B12 or the shaft bearing B23, which are replaced here by a toothed axial pin 31 extending downward. These transmission devices 3 also include a toothed wheel 32, which is mounted on a horizontal rotation axis 33, which is received in a fixed shaft bearing P33 formed by a fixed part of the dispenser. These transmission devices 3 also include two actuating cams 35, which engage with the actuating pin P21 and more particularly with the edge P211 of the actuating pin. The toothed pin 31 meshes with the toothed wheel 32, so that an axial displacement of the common piston B" has the effect of rotating the toothed wheel 32 about its axis 33, thus causing a pivotal displacement of the two actuating cams 35 acting directly on the actuating pin P21. Here too, as in the first two embodiments of the invention, the contact surfaces 351 of the two actuating cams 35 can be profiled so as to adjust the displacement speed of the actuating pin P21 relative to the displacement speed of the other actuating pin P11 directly acted upon by the common piston B″.

[0058] In the three embodiments described above, the two actuating pins P11 and P21 can be displaced simultaneously throughout their respective strokes, but at different displacement speeds. However, it is not excluded that the displacement speeds of the two pins can be the same within a portion of the stroke of the two pins. However, it can ultimately be said that the displacement speed of the actuating pin P21 is reduced relative to the displacement speed of the other actuating pin P11. The actuating speeds of the two pins can be proportional or linear to a regular contact surface, or conversely non-proportional or non-linear to a complex contact surface. The advantage of the first embodiment with the movable element 1 is that only one single part is added to the double dispenser: the rotation axis B12 and the curved inclined ramp P14 can be made as a single piece together with their corresponding components.

[0059] The invention thus provides a double dispenser with different pumps and a common axial piston, from which two doses can be dispensed simultaneously despite the different strokes of the actuating pins of the two pumps.

Claims

1. A dual dispenser, comprising two pumps (P1, P2), namely: a first pump (P1) provided with a first actuating pin (P11) axially displaceable within a first maximum stroke, and a second pump (P2) provided with a second actuating pin (P21) axially displaceable within a second maximum stroke, The dispenser comprises a common piston (B; B’； B”), the common piston (B; B’； B″) is axially displaceable and acts axially and directly on the first actuating pin (P11) in order to drive the first actuating pin (P11) within the first maximum stroke of the first actuating pin (P11), It is characterized in that - the first maximum stroke is greater than the second maximum stroke, and -The distributor also includes a reduction transmission device (1; 2; 3), which acts between the common piston (B; B'; B") and the second actuating pin (P21) so as to transmit the axial driving force of the common piston (B; B'; B") to the second actuating pin (P21), wherein the speed of the second actuating pin (P21) is reduced relative to the speed of the first actuating pin (P11), and the speeds of the actuating pins (P11, P21) are different and not zero.

2. The dispenser according to claim 1, wherein: The reduction transmission device (1; 2; 3) includes an actuating cam (15; 25; 35), which is in contact with the second actuating pin (P21) so as to shift the second actuating pin (P21) within the second maximum stroke of the second actuating pin (P21), and the actuating cam (15; 25; 35) includes a contact surface (151, 152; 251; 351) in dynamic contact with the second actuating pin (P21), and the contact surface (151, 152; 251; 351) has a profile that affects the displacement speed of the second actuating pin (P21).

3. The dispenser according to claim 1, wherein: The reduction transmission device comprises a movable element (1), which rotates around a vertical rotation axis (B12) fastened to the common piston (B), and the movable element (1) comprises: - an axis housing (12) of the vertical rotation axis (B12) of the common piston (B), - a rotary drive member (14) which is in sliding contact on a fixed curved inclined ramp (P14), and - an actuating cam (15) which is in sliding contact with said second actuating pin (P21).

4. The dispenser according to claim 3, wherein: The actuating cam (15) comprises a contact surface (151, 152) engaging with the second actuating pin (P21), the contact surface (152) being at least partially inclined.

5. The dispenser according to claim 3 or 4, wherein: The contact surface (151) is partially planar.

6. A dispenser according to claim 3, 4 or 5, wherein: The movable element (1) is made in one piece.

7. The dispenser of claim 3, 4, 5 or 6, wherein: The movable element (1) is biased in a rotational manner towards a starting position by a return spring (13), which is advantageously made in one piece with the movable element (1).

8. The dispenser according to any one of claims 1 to 4, wherein The reduction transmission device (2) comprises two hinged rods (21, 22) connected together at a common joint (20), namely a first rod (21) and a second rod (22), wherein the first rod (21) is hinged on a pivot (B23) fastened to the common piston (B'), and the second rod (22) is hinged on a fixed pivot (P24), and the common joint (20) is provided with an actuating cam (25) which contacts the second actuating pin (P21).

9. The dispenser according to any one of claims 1 to 4, wherein: The reduction transmission device (3) comprises: - a toothed wheel (32) mounted on a fixed horizontal rotation axis (33), a toothed axial pin (31) fastened to the common piston (B") and engaging with the toothed wheel (32) so as to drive the toothed wheel (32) in rotation, and - an actuating cam (35) fastened to said toothed wheel (32) and in contact with said second actuating pin (P21).

10. The dispenser according to any one of the preceding claims, wherein The first maximum stroke and the second maximum stroke are performed completely and simultaneously by axially pushing the common piston (B; B'; B").

11. The dispenser according to any one of the preceding claims, wherein The velocity V2 of the second actuating pin (P21) is proportional to the velocity V1 of the first actuating pin (P11), such that V2=K×V1, where K is a constant less than 1.

12. The dispenser according to any one of claims 1 to 10, wherein The velocity V2 of the second actuating pin (P21) is not proportional to the velocity V1 of the first actuating pin (P11), such that V2=f(x)×V1, wherein f(x) varies between 0 and 1.

Images