HIGH-PRESSURE PRE-COMPACTION PUMP

Description

[0001] The present invention relates to a fluid product dispensing device comprising a spray nozzle with several dispensing orifices and a pump for dispensing metered quantities of the fluid product. More particularly, the pump is a pre-compression pump in which the fluid product is dispensed at a high pressure of at least 15 bar. The present invention also relates to the method of assembling such a pump.

[0002] Fluid product dispensing devices with dispensing nozzles having a plurality of dispensing orifices or holes are known, in particular, from documents EP1878507 and WO2018100321. In these documents, the diameter of the holes is generally between 8 and 20 µm. In document EP1878507, the nozzle is associated with a pre-compression pump delivering the fluid product to the nozzle at a pressure of less than 7 bar. In document WO2018100321, the nozzle is associated either with a pump operating at a pressure between 2 and 7 bar or with a pressurized valve operating with a propellant gas at a pressure between 6 and 13 bar. Depending on the nozzle configuration, particularly for holes with a diameter of less than 5 µm, these pressures may be insufficient to ensure optimal operation of the device.Furthermore, it may be advisable to use a pre-compression pump to avoid the propellant gases from the valves, which are potentially harmful to the user and / or the environment. Documents EP1698399, WO2015194962, and WO2018219798 describe other examples of micro-hole nozzles.

[0003] Documents WO2014125216, WO0102100, WO8704373, and EP0265270 disclose pumps in which the dispensing of the fluid product is independent of the speed and / or force of the user's actuation. During pump actuation, a spring is compressed by the pressure created inside the pump chamber. This spring is released at the end of the actuation cycle after an outlet valve opens, so that the dose of product contained in the pump chamber is expelled by the spring, regardless of the user's actuation speed. Typically, these pumps deliver a pressure of approximately 6-7 bar.

[0004] The present invention aims to provide a device and a pump that do not reproduce the aforementioned disadvantages.

[0005] The present invention aims in particular to provide a fluid product distribution device allowing a manually operated pre-compression pump delivering high pressure to be combined with a distribution nozzle having several distribution orifices.

[0006] The present invention also aims to provide a pump that delivers the fluid product at a higher pressure compared to traditional pumps.

[0007] The present invention also aims to provide such a pump which is simple and easy to manufacture and assemble, and reliable in its use.

[0008] The present invention also aims to provide such a pump which ensures a total and reproducible distribution of the contents of the pump chamber at each actuation, regardless of the user's actuation speed.

[0009] The present invention also aims to provide a method for assembling such a pump which improves the reliability of the pump during storage and use, in particular by improving the integrity of parts subjected to high pressure during actuation.

[0010] The present invention relates to a fluid product distribution pump according to claim 1. Advantageous embodiments are described in the dependent claims. The present invention also relates to a fluid product distribution device comprising a pump as described above.

[0011] These and other features and advantages of the present invention will become more apparent from the following detailed description, made with reference to the accompanying drawings given by way of non-limiting examples, in which: there figure 1 is a schematic cross-sectional view of a pump according to the prior art, in its rest position, the figure 2 is a partial schematic cross-sectional view of the pump of the figure 1 during the assembly of the upper piston, the figure 3 is a schematic cross-sectional view of a fluid product distribution device according to an advantageous embodiment, the figure 4 is an enlarged cross-sectional detail view of a part of the pump shown on the figure 3 , there figure 5 is an enlarged perspective detail view of another part of the pump shown on the figure 3 , THE figures 6 to 9are schematic cross-sectional views of a pump according to a first advantageous embodiment, respectively in the rest position, at the beginning of the actuation stroke, during the actuation stroke, and at the end of the actuation stroke. Figures 10 and 11 are schematic cross-sectional views of a pump according to an advantageous embodiment of the present invention, respectively in the rest position and at the end of the actuation stroke, Figures 12 and 13 are partial schematic cross-sectional views of the pump of the figure 6 , respectively during and at the end of upper piston assembly, and the figure 14 is a partial schematic cross-sectional view of the pump of the figure 6 lower piston assembly in progress.

[0012] The various aspects of the present invention will be described with reference to several embodiments. It is understood, however, that the present invention is not limited by the embodiments shown in the drawings.

[0013] THE figures 1 and 2 illustrate a pump from earlier art, according to document WO2014125216.

[0014] With reference to figures 1 and 2 This prior art pump comprises a pump body 3 in which a piston 1 slides, attached to an actuating rod 2 which the user presses to operate the pump. The piston 1 slides in a pump chamber 5 defined in the pump body 3 between an inlet valve 11 and an outlet valve 12. A mounting ring 4, for example crimpable, screwable or snap-on, allows the pump to be fixed to a tank.

[0015] The inlet valve 11, open in the pump's rest position, as seen on the figure 1, is formed by a movable inlet valve element 10 within the pump body 3 during pump actuation and adapted to cooperate with a part of the pump body 3 at the beginning of pump actuation to close said inlet valve 11. Said inlet valve element 10 is made in the form of a hollow cylinder closed on one side by a bottom wall, the edge of the open end of said hollow cylinder cooperating in a sealed manner from the beginning of pump actuation with a cylinder 9 of the pump body 3 to close the inlet valve 11. A spring 20 bears on one side against a bottom wall of the inlet valve element 10 and on the other side against a part of the pump body 3.

[0016] The outlet valve 12 comprises an outlet valve element 39, advantageously formed by the lower lip of the piston 1, and is designed such that, during pump actuation, it opens only at the end of the pump stroke to allow the expulsion of the product contained in the pump chamber. This opening is made at the level of passage means formed at the level of an internal radial shoulder 40 of the pump body. The purpose of said passage means 40 is to form at least one fluid passage when the outlet valve element 39, which throughout the pump actuation stroke cooperates in a sealed manner with the pump body 3, reaches the end of its actuation stroke at the level of said passage means 40.

[0017] The expulsion of the product contained in the pump chamber 5 is carried out independently of the actuation speed applied by the user. To achieve this, the inlet valve element 10 cooperates with the spring 20, which, during pump actuation, is compressed by the displacement of the inlet valve element 10 under the effect of the pressure created in the pump chamber. At the end of the pump's actuation stroke, when the outlet valve 12 is opened, the compressed spring 20 is abruptly released, so that the product contained in the pump chamber is expelled via this spring. Advantageously, the spring 20 of the inlet valve 11 also acts as a return spring for the pump, thus returning the piston 1 to its rest position after the product has been expelled.

[0018] The pump of figures 1 and 2It therefore comprises two pistons, on the one hand piston 1, part of which defines the outlet valve, and on the other hand the inlet valve element 10 defining the inlet valve, and which during actuation acts as a piston against the external surface of the cylinder 9 of the pump body 3.

[0019] In the figure 2 As can be seen during assembly, the two pistons are fitted into the body from above. Thus, the lower lip 39 of piston 1, which forms the outlet valve element, comes into contact with the inlet of the pump body 3, which can weaken this lip. The lip 39 is oriented axially downwards in the position of the figure 2It is necessarily the radially external end part that provides the seal and comes into contact with the pump body during assembly. Depending on the force with which this part is assembled into the pump body, its integrity can be compromised, which may reduce its sealing capacity, particularly at high pressures.

[0020] Similarly, the inlet valve element 10 is also assembled around the sleeve 9, with its sealing lip striking the upper edge of said sleeve. Here too, there is a risk of damaging the sealing surface of this lip, and therefore impairing the sealing performance of said inlet valve element.

[0021] This pump from earlier art, depicted on the figures 1 and 2typically delivers a pressure of approximately 7 bar. This pressure P is equal to the spring force F divided by the surface area S over which it is applied, according to the formula P = F / S. In the example of the pump... figures 1 and 2 The spring 20 typically has a force F of 13 N, and the surface area S, which corresponds to the outer diameter of the sleeve 9 around which the valve element 10 will slide during actuation, is typically 18.8 mm² (the outer diameter of the sleeve 9 being typically 4.9 mm). The pressure P is therefore approximately 7 bar. By modifying the spring 20, for example by using a spring with a force of 25 N, a pressure of approximately 13 bar could be achieved. However, this is hardly feasible for several reasons. Firstly, due to its dimensions, actuation of such a 25 N spring in the pump of the figure 1This could become difficult, especially for elderly or frail users. Furthermore, such an increase in pressure might not be able to withstand the two pistons, whose sealing lips are susceptible to damage during pump assembly (see above). The risks of leaks and malfunctions would be too high, preventing reliable dispensing of complete doses of fluid product with each actuation.

[0022] The present invention relates in particular to a pre-compression pump adapted to deliver a pressure of at least 15 bars, advantageously of at least 20 bars.

[0023] To do this, the pump of the prior art of figures 1 and 2 is modified both structurally and functionally as will be described below. Identical or similar parts are identified on the figures 3 to 14 using the same numerical references.

[0024] As in the pump of the figures 1 and 2The pump according to the invention comprises a pump body 3 in which a piston 1 slides, attached to an actuating rod 2 which the user presses to operate the pump. The piston 1 slides in a pump chamber 5 defined in the pump body 3 between an inlet valve 11 and an outlet valve 12. A mounting ring 4, for example crimpable, screwable or snap-on, allows the pump to be fixed to a tank.

[0025] The side wall of the pump chamber 5 is reinforced by the insertion of a sleeve 50 into the pump body 3. This sleeve 50 is formed as a single piece with the retaining ring 4. This sleeve 50 thus forms a double wall within the pump chamber 5, which prevents deformation of the internal side wall of the pump chamber 5 due to the high pressure created by the pump during operation. This sleeve 50 includes the radial shoulder that defines the outlet valve 40. Advantageously, as can be seen in the figure 4 , to avoid any leaks between the sleeve 50 and the pump body 3, a watertight weld 55 is provided, for example by ultrasound, preferably between two radial flanges respectively of said pump body 3 and of said fixing ring 4 which incorporates the sleeve 50.

[0026] Similarly, the sleeve 9, which cooperates with the inlet valve element 10, extends axially downwards from the pump body 3 in the orientation of the figures 6 to 14 and contains said inlet valve element 10 and said spring 20. The inlet valve element 10 is solid and has peripheral sealing lips extending radially outwards. In the rest position, visible in particular on the figure 6 These sealing lips do not form a tight seal with the sleeve 9, so the inlet valve 11 is open. During actuation, the valve element 10 slides axially within the sleeve 9, compressing the spring 20. This sliding motion is achieved in a tight seal, as the sealing lips of the valve element 10 form a tight seal with the sleeve 9.

[0027] The sleeve 9 has a reduced diameter compared to the pump body 3. It advantageously features external reinforcing ribs 90, visible in particular on the Figures 5 And 7 à 9This implementation of sleeve 9 allows for a reduction in its radial dimensions, typically with an internal diameter smaller than the external diameter of sleeve 9 of the pump. figure 1 For example, sleeve 9 of the pump of the figure 6 could have a diameter of less than 4.2 mm, advantageously less than 4 mm, preferably 3.9 mm.

[0028] The piston 1 and the outlet valve element 39 could be made from a single piece, but preferably as shown in the figures 3 And 6 à 14 The outlet valve element 39 is formed by a separate part that is fixed within the piston 1. This fixing can be achieved by press fitting, snap-fit, screwing, or any other suitable fastening. The sealing lips of the piston 1 and the outlet valve element 39 are oriented in the same direction, downwards in the position of the figure 6 .

[0029] One of the features of the pump according to the invention is the assembly of the piston 1 and the outlet valve element 39 in the sleeve 50. Unlike the pump of the figures 1 and 2 This assembly is done from the bottom, as can be seen on the Figures 12 and 13 Thus, the sealing lips are not weakened by this assembly, as they are oriented in the opposite direction to the assembly direction. In this way, the elastic deformation of the sealing lips is not achieved by frontal contact of the radially external surface of the lips against the sleeve 50 of the pump chamber 5, but rather, the lips are progressively deformed radially inwards, so that the sealing surfaces are not subjected to any sudden stress that could impair their sealing capacity.

[0030] The inlet valve element 10 has sealing lips oriented in the opposite direction to the sealing lips of the piston 1 and the outlet valve element 39. As can be seen in the figure 14 The said inlet valve element 10 is assembled into the sleeve 9 of the pump body from above. In this way, its sealing lips are not damaged during assembly.

[0031] The pump according to the invention therefore significantly improves the sealing capabilities of the various sealing parts, namely the piston 1, the outlet valve element 39 and the inlet valve element 10.

[0032] Thus, it becomes possible to use a spring with a greater force, typically at least 20 N, advantageously 25 N.

[0033] With an internal diameter of sleeve 9 of 3.9 mm, corresponding to a surface area of ​​12 mm², and a 20 N spring, the pressure P is approximately 16.5 bar. With a 25 N spring, the pressure rises to approximately 21 bar.

[0034] Thus, the present invention makes it possible to provide a standard type pre-compression pump but capable of distributing the fluid product at a pressure of at least 15 bars, advantageously about 20 bars, which is much higher than traditional standard pumps and even higher than valves operating with a propellant gas.

[0035] The actuation force of such a pump with a spring of 25 N and the surface S of 12 mm² is less than 60 N, advantageously about 50 N, which remains acceptable.

[0036] The present invention also provides an advantageous assembly method. This assembly method comprises the following steps: supply the piston 1 integral with the actuating rod 2; supply the pump body 3 comprising the pump chamber 5; supply the sleeve 50, advantageously integral with the fixing ring 4; supply the outlet valve element 39 sliding during actuation in a sealed manner in the pump chamber 5; supply the inlet valve element 10 sliding in the sleeve 9 of the pump body 3, said sleeve 9 having a reduced diameter; supply the spring 20.

[0037] The process also includes the following steps: fix the outlet valve element 39 in the piston 1; insert the piston 1 and the outlet valve element 39 into the sleeve 50, said insertion being made from below, in the direction of fluid flow during its expulsion; insert the spring 20 and the inlet valve element 10 into the reduced diameter sleeve 9, said insertion being made from above, in the opposite direction to the fluid flow during its expulsion, so as to wedge the spring 20 between the bottom of the sleeve 9 and the inlet valve element 10; insert the sleeve 50 into the pump body 3, said insertion being made from above, in the opposite direction to the fluid flow during its expulsion.

[0038] Optionally, the step of inserting the spring 20 and the inlet valve element 10 into the reduced diameter sleeve 9 can be carried out before the step of inserting the piston 1 and the outlet valve element 39 into the sleeve 50.

[0039] The operation of the pump is illustrated on the figures 6 to 9 .

[0040] The resting position is visible on the figure 6 , with the inlet valve 11 open and the outlet valve 12 closed.

[0041] At the start of activation, visible on the figure 7 The inlet valve 11 closes through a tight seal between the lips of the inlet valve element 10 and the internal cylindrical surface of the sleeve 9, while the outlet valve 12 remains closed. The spring 20 is compressed by the inlet valve element 10 sliding within the sleeve 9. Since the sleeve 9 has a smaller diameter than the sleeve 50 located in the pump body 3, and the fluid contained in the pump chamber 5 is incompressible, this compression of the spring 20 occurs relatively easily, despite the high force of said spring 20.

[0042] When approaching the end of the actuation, as visible on the figure 8, the outlet valve element 39 approaches the shoulder 40 of the outlet valve, to open it.

[0043] There figure 9 This illustrates the actuated position, with the outlet valve open and therefore the contents of the pump chamber 5 being expelled under the effect of the spring 20 as it relaxes. The fluid product is then expelled with a pressure of at least 15 bar, advantageously at least 20 bar.

[0044] THE Figures 10 and 11 They show an alternative embodiment in which a second spring 80 is provided to assist the user in their actuation effort, thereby reducing it. In this embodiment, the second spring 80 is advantageously positioned around the piston 1 to move it towards its actuated position. The second spring 80 thus acts against the spring 20, and consequently its force must be less than that of spring 20.

[0045] With such a second spring 80, one could consider using an even more powerful spring 20, for example with a force F greater than 30 N, advantageously even greater than 35 N, for example 38 N, which, for a surface S of 12 mm², would allow pressures P greater than 25 bars, advantageously greater than 30 bars, for example 32 bars.

[0046] Advantageously, the piston 1 can be integral with an external sleeve 2' assembled around the actuating rod 2, itself integral with the outlet valve element 39. This implementation could also be adapted to the variant of figures 6 to 9 .

[0047] The present invention also relates to a fluid product distribution device comprising a pump as described above, associated with a spray nozzle having a plurality of distribution orifices.

[0048] The use of a micro-hole nozzle, such as the one described in document WO2018100321, may, depending on the nozzle design, and particularly if the micro-holes have a diameter of less than 5 µm, or even less than 2 µm, require a fluid arriving at a high pressure, typically exceeding 15 bar. The present invention makes it possible to guarantee a pressure of at least 15 bar, advantageously at least 20 bar, without using a propellant gas.

[0049] As seen on the figure 3 , the device comprises a body 101 containing a reservoir 100, on which is mounted a pump as described above, by means of the fixing ring 4.

[0050] The reservoir 100 is preferably air-free. Advantageously, a deformable pouch 105 is attached inside said reservoir 100, said pouch containing the fluid product and deforming as doses are dispensed. Preferably, the pouch can be filled under vacuum. This implementation ensures that almost all of the product contained in the pouch is delivered, allows the device to be operated in any orientation, and avoids any risk of contamination of the fluid product contained in the pouch. As an alternative to the pouch, a follower piston could also be used in the reservoir 100.

[0051] Alternatively, a device operating with an air intake could also be used, in which case a filter would be advantageously provided to filter the ventilation air.

[0052] A micro-perforated nozzle 200, the operation of which will not be described in further detail below, but which can be of any known type, such as those described, for example, in documents EP1878507, WO2018100321, EP1698399, WO2015194962, or WO2018219798, is arranged in a dispensing nozzle 110 fixed to the body 101. This dispensing nozzle 110 can, for example, be a mouthpiece. Typically, the fluid expelled by the pump strikes a plate perforated with a plurality of micro-perforations, which generates the atomization of the fluid.

[0053] The micro-holes of the 200 nozzle have a diameter of less than 5 µm, preferably less than 2 µm.

[0054] Advantageously, a filter 150 is interposed between the pump outlet and the nozzle 200. This filter serves to remove impurities that could be carried by the fluid as it passes through the various plastic parts. Indeed, there is always a risk that particles will be generated during the manufacturing and assembly processes, potentially clogging the nozzle's micro-holes.

[0055] Advantageously, the body 101 has a lateral actuation arm 160, which allows the pump to be operated by lateral actuation.

[0056] Of course, the invention is not limited to the embodiments shown in the drawings, and the scope of the invention is instead defined by the attached claims.

Claims

1. A pump for dispensing a fluid product comprising a piston (1) secured to an actuation rod (2) and which slides in a pump body (3) having a pump chamber (5) defined between an inlet valve (11) and an outlet valve (12), said outlet valve (12) comprising an outlet valve element (39) sliding during actuation in a sealed manner in the pump chamber (5), said pump chamber (5) comprising passage means (40) so that, at the end of actuation of the pump, said outlet valve element (39) co-operates in a non-sealed manner with said passage means (40) in order to open said outlet valve (12) to allow the expulsion of the product contained in the pump chamber, said inlet valve (11) comprising an inlet valve element (10) which slides after closure of the inlet valve (11) in a sleeve (9) of the pump body (3), said sleeve (9) having a reduced diameter with respect to said pump body (3) and containing a spring (20) bearing firstly on said inlet valve element (10) and secondly on a bottom of said sleeve (9), said spring (20), in addition expelling the product, also returning the piston (1) into its rest position, and a second sleeve (50) inserted into said pump body (3) characterised in that said sleeve (9) has an inner diameter of less than 4.2 mm, advantageously less than 4 mm, preferably 3.9 mm, said spring (20) is configured to exert a force of at least 20N, advantageously at least 25N, so that said pump dispenses said fluid product at a pressure (P) of at least 15 bars, advantageously at least 20 bars, said second sleeve (50) being inserted into said pump body (3) to reinforce the side wall of said pump chamber (5), said second sleeve (50) being formed in one piece with a fixing ring (4) configured to fixing said pump to a reservoir, said second sleeve (50) including a shoulder defining said passage means (40) of said outlet valve (12).

2. The pump according to claim 1, wherein a sealed weld (55), for example by ultrasound, is provided between said pump body (3) and said second sleeve (50), advantageously between two respective radial flanges of said pump body (3) and said second sleeve (50).

3. The pump according to 1 or claim 2, wherein said outlet valve element (39) is fixed in said piston (1).

4. The pump according to any preceding claim, wherein said sleeve (9) of the pump body (3) in which said inlet valve element (10) slides includes external reinforcing ridges (90).

5. A product fluid product dispensing device, characterized in that it includes a pump according to any one of preceding claims.