RU2452672C2 - Throwaway pump with fluid return suction device - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: proposed pump is intended for compressible fluid dispensing system and comprises chamber with variable pressure to suck fluid from tank into chamber and from chamber into dispensing orifice, encased valve to regulate fluid flow between tank and chamber, inner and outer valves to regulate fluid flow between chamber and dispensing orifice. Said pump may change over from closed position into dispensing position. Inner and outer valves are arranged on regulator fixed in case. Said case houses chamber and dispensing orifice to create negative pressure when pump changes from dispensing position into closed position. Pressure difference between tank and chamber causes opening of inner valve to allow fluid flow from tank into chamber while pressure difference between dispensing orifice and chamber causes opening of outer valve to allow return suction of fluid from dispensing orifice into chamber.

EFFECT: higher reliability, simplified assembly.

12 cl, 22 dwg

Description

Technical field

The present invention relates to a disposable pump for a metering system for liquids, in particular for a metering system that contains a compressible container.

BACKGROUND OF THE INVENTION

The present invention relates to the field of disposable suction pumps for dispensing a liquid substance, such as soap or alcohol detergent, from a container, such as a bottle or the like. A large number of different suction pumps have been proposed in the past. Typically, many suction pumps include a pressure chamber from which a volume of liquid can be dispensed. The liquid exiting the chamber creates a negative pressure in the fluid chamber, and this negative pressure performs the function of absorbing a new fluid from the reservoir into the pressure chamber, which is thus filled and becomes ready to dispense a new volume of fluid.

During use, the container is connected to the pump and inserted in a metering device, which is usually located motionless on a wall in a bathroom or the like. Some metering devices include a collapsible pump that is integral with the metering device and with which disposable containers can be connected. In contrast, the present invention relates to a disposable pump that can be connected to a disposable tank for attachment to a fixed (reusable) metering device.

One type of metering device includes a drive device for driving a pump and dispensing a volume of liquid. Another type of metering device is positioned so that part of the pump exits the metering device, showing a drive device that is integral with the pump. Usually, two types of drive devices are used, or made integrally with a metering device or with a pump.

One type is a drive device operating in the longitudinal direction. "In the longitudinal direction" refers in this context to a direction parallel to the dispensing direction and the pump outlet. Pumps for longitudinal actuation often contain a sliding piston that can be extended / retracted in the longitudinal direction to decrease / increase the volume inside the pump pressure chamber, resulting in a pumping effect. When performing the drive device as a whole with the pump, it may contain an outlet for dispensing liquid.

Another type of drive device is a drive device operating in the transverse direction. "In the transverse direction" refers in this context to the direction transverse to the dispensing direction and the outlet of the pump. Pumps for transverse actuation usually should be located in a fixed metering device, which contains a drive device acting in the transverse direction. The driving device acting in the transverse direction may be a rod or the like, which after transverse displacement performs the function of reducing the volume inside the pump pressure chamber.

Like pumps, tanks are known in a wide variety of forms. One particular type of reservoir is compressible reservoir, which is designed to be gradually compressed, reducing its internal volume when dispensing fluid from them. Compressible containers are particularly advantageous, taking into account hygiene requirements, since the integrity of the container is maintained during the entire drainage process, which ensures that no contaminants penetrate it and that any faking of the contents of the container is not possible without visible damage to the container. The use of compressible containers includes specific pump requirements. In particular, the suction force generated by the pump must be sufficient not only to dispense the liquid, but also to compress the container. In addition, negative pressure can be created in the tank, tending to expand the tank to its original shape. Therefore, the pump must also be able to overcome negative pressure.

One type of compressible container is a simple bag, usually made of some soft plastic. The bags are usually relatively easy to compress, and the walls of the bag will not tend to straighten after compression, therefore, the walls of the bag will not contribute to any negative pressure in the bag.

Another type of compressible containers is known from, for example, EP 0072783 A1 and DE 9012878 U1. This type of compressible containers contains at least one relatively rigid wall to which the compression of the remaining less rigid walls of the container will be directed. Therefore, hereinafter, this type of tank is called a semi-rigid compressible tank. This type of compressible containers is advantageous in that the information can be printed on a rigid wall so that the information remains clearly visible and undistorted regardless of the state of compression of the container. In addition, for some contents, containers containing at least one relatively rigid wall can preferably be used instead of bags. However, for compressible containers containing at least one relatively rigid wall, a large suction force created by the pump may be required to overcome the negative pressure created in the vessel during emptying, compared to bags.

For single-use pumps, there is a basic need for the pump to be relatively lightweight and economical to manufacture. In addition, it is preferable if the pump includes materials that can be easily disposed of after removal, and even more preferably, if the pump can be disposed of as a single device without the need to separate its parts after removal.

EP 1215167 describes a single-use pump containing four plastic parts, each part being made using extrusion pressing methods. The first part includes a connector made with a thread for screwing on the bottle. An outlet extends from the connector, said outlet ending with a perforated plate through which contents from the bottle can pass. The first part also includes a rod extending from the perforated plate. The second part is screwed onto the shaft and includes two diaphragms arranged one after another to form pump valves. The third extruded part includes a pressure chamber, which is connected to the first part, so that the rod is inserted into the chamber, and the membranes come into tight contact with the inner walls of the pressure chamber. Finally, a fourth extruded part made of an elastic material is connected to the outer wall of the pressure chamber and is in fluid contact with it. The fourth extruded portion includes a convexity of compression, which when pressed increases the pressure in the pressure chamber.

The EP 1215167 pump includes four parts that can be made from similar, but not the same materials. However, the pump EP 1215167 is not able to create a suction pressure sufficient to empty the compressible tank, since negative pressure in the compressible tank will prevent expansion of the compression bulge, and therefore, the pump function will be significantly impaired when used with a compressible tank.

EP 0854685 describes another single use pump. The pump is made of two single elements made entirely of plastic for single use as a single device. The two elements are the chamber, which includes a housing and a piston containing a shaft and two single-acting valves. The piston is slidably housed in a chamber including a housing, and liquid is supplied from the reservoir by moving outward and inward of the piston in a chamber including the housing. This application explains that if positive pressure is maintained inside the tank to which the pump is connected, the pump will reciprocate, for example, manually applied forces can be used to move the piston inward, overcoming the pressure in the tank, and the pressure in the tank will push the regulator outward during the return stroke.

From the above description it is clear that if negative pressure is maintained inside the container, as would be the case when using a compressible container, the piston will not be able to return automatically, which means that the flow of fluid from the pump is relatively complicated.

Therefore, none of the above pumps is satisfactory for use with a compressible tank. In addition, well-known pumps that are used for compressible containers are relatively expensive, including a large number of elements and often a large assortment of materials.

In view of the foregoing, there is a need for disposable pumps that can be easily disposed of and which are suitable for use with a compressible container, in particular a semi-rigid type container. Preferably, the pump should be returned so that it is not necessary to exert force from the outside to return the pump to a filling state after dispensing the liquid.

Advantageously, the pump should be suitable for pumping liquids of various viscosities, from substances with a low viscosity, such as alcohol, to substances with a high viscosity, such as liquid soap.

Preferably, the pump should be driven using a transverse drive device.

Preferably, the pump should be airtight. Advantageously, the pump should include a liquid back suction device for additional protection against leakage.

An object of the present invention is to provide a pump that satisfies one or more of the above requirements.

A brief description of the present invention

This goal is achieved by a pump for a metering system for liquids, in particular for a metering system that contains a compressible tank, in which the pump contains a chamber in which the pressure can be changed to pump liquid from the tank to the chamber and, then, from the chamber to the metering hole moreover, the chamber contains an internal valve for regulating the fluid flow between the container and the chamber, and an external valve for regulating the fluid flow between the chamber and the metering hole in which the pump can

- a closed position in which the volume of liquid is supplied from the tank into the chamber under the influence of the negative pressure created in the chamber, and

- a dispensing position in which a volume of liquid is supplied from the chamber to the dispensing opening;

wherein

the internal valve is a one-way valve for opening for fluid flow in the dispensing direction at the opening pressure of the internal valve acting in the dispensing direction and closing at any pressure acting in the direction opposite to the dispensing direction,

the outer valve is a two-way valve for opening for fluid flow in the dispensing direction or in the direction opposite to the dispensing direction at the opening pressure of the external valve, depending on the direction of opening pressure of the external valve,

so as the pump moves from the dispensing position to the closed position and negative pressure is created in the chamber,

the pressure difference between the vessel and the chamber will cause the opening of the internal valve to allow fluid to flow from the vessel to the chamber, and

the pressure difference between the metering orifice and the chamber will cause the external valve to open to allow the liquid to return from the metering orifice to the chamber.

Usually a negative pressure is created in the chamber when it is empty, that is, when the liquid was dosed from the pump. In this situation, the remainder of the liquid may be near the metering opening. In the case of the proposed pump, the pressure difference between the metering hole and the negative pressure in the chamber will cause the opening of the external valve, and any remaining liquid will be sucked back into the chamber.

Mostly, the pump is designed so that

- when the pump is in its dispensing position, the outer valve forms said two-way valve, and

- when the pump is in its closed position, the outer valve seals between the chamber and the metering hole,

so that when the pump moves from the dispensing position to the closed position, the external valve will first open to allow liquid to be sucked back from the dispensing hole into the chamber, and then, when the closed position is reached, seal between the chamber and the dispensing hole.

In this embodiment, it is ensured that the re-filling of the liquid from the container when controlled by the internal valve can prevail over the re-absorption of the liquid and, then, the air from the metering opening. The chamber is typically designed to be re-filled with liquid from a container, rather than air from an opening. Therefore, it is necessary that the external valve is opened to provide reverse suction of the liquid only for a flow that is much smaller than the fluid flow from the tank when regulated by the internal valve. In accordance with the proposed embodiment, the outer valve can open for flow in the direction opposite to the metering direction only for a short period of time when the pump moves from the metering position to the closed position. However, the internal valve may continue to open for flow in the dosing direction also when the pump has reached the closed position.

Advantageously, when the pump is in its dispensing position, the outer valve takes an inclined position in the chamber, and when the pump is in its closed position, the outer valve assumes a symmetrical position in the chamber. In the tilted position, the opening pressure of the outer valve may be less than in the symmetrical position, so that reverse suction can occur when the valve is in its tilted position, and not when it is in its symmetrical position. During the transition of the pumps from the metering position to the closed position, the outer valve can move from an inclined position to a symmetrical position. This means that the external valve can be opened at first to provide back suction, and at the end it closes when a symmetrical position is reached.

Alternatively, or in addition to the foregoing, the opening pressure of the internal valve may be less than the opening pressure of the external valve, so that the external valve will close before the internal valve when the negative pressure in the chamber is equalized.

Advantageously, the internal valve when in the closed position may have a contact area with the chamber greater than the contact area of the external valve when in the closed position.

Advantageously, the external valve, when in the closed position in the chamber, is compressed peripherally with respect to the uncompressed state of the external valve, and the difference between the diameter of the chamber at the location in which it is in contact with the external valve when it is in the closed position and the diameter of the external valve, when it is in an uncompressed state, it is 0.09-0.20 mm, preferably 0.10-0.20 mm, most preferably 0.10-0.15 mm.

Advantageously, the inner valve, when in the closed position, is compressed around the periphery relative to the uncompressed state of the inner valve, and the difference between the diameter of the chamber at the location where the inner valve is compressed around the periphery and the diameter of the inner valve when it is uncompressed is 0 , 20-0.35 mm in the peripheral direction, preferably 0.25-0.35 mm, most preferably 0.25-0.30 mm.

Preferably, the inner valve is a parabolic valve. The parabolic valve is suitable as a one-way valve that can tightly seal in one direction.

Advantageously, the inner valve comprises an edge that is capable of moving into tight contact with and from the chamber, said edge forming an angle with the longitudinal axis of the pump, where the angle is in the range of 15-30 degrees, more preferably 20-30 degrees, most preferably 20- 25 degrees.

Advantageously, the outer valve may have an outer shape at least partially repeating the contour of the ball. Typically, the spherical shape is advantageous for the function as a two-way valve, since the opening can be carried out in two opposite directions.

Preferably, the outer shape of the outer valve follows the contour of the ball to form at least half of the ball.

Advantageously, the outer valve comprises an edge that is able to move into tight contact with and from the chamber, and said edge, when the pump is in its closed position, is held between the parallel walls of the chamber and runs parallel to the walls.

In addition, the present application describes a disposable pump for a metering system for dispensing liquids, in particular for a metering system that comprises a compressible container in which the pump contains

- a housing including a chamber and a metering hole, in which the pressure in the chamber can be changed to pump liquid from the tank into the chamber and, then, from the chamber into the metering hole, and

- a regulator located stationary in the chamber for regulating the flow of fluid between the container and the chamber and between the chamber and the metering hole, and the controller contains

- an external valve for regulating the flow between the chamber and the metering hole,

in which the pump can take

- a closed position in which the volume of liquid is supplied from the tank into the chamber under the influence of the negative pressure created in the chamber, and

- a dispensing position in which a volume of liquid is supplied from the chamber to the dispensing opening;

wherein

the external valve is able to move between

- a symmetrical position, which corresponds to the aforementioned closed position of the pump, in which the external valve is in close contact with the housing, and

- an inclined position, which corresponds to the aforementioned dosing position of the pump, in which the external valve is able to move into tight contact with and out of the housing depending on changes in pressure in the chamber, and

moving said external valve from said symmetrical position to said inclined position requires an external force applied to the pump and transmitted to said regulator regardless of changes in pressure in the chamber.

In the pump, as suggested above, dosing of liquid will occur only when the external valve is in its inclined position, and if at the same time the pressure in the chamber is large enough to open the external valve. When the external valve is in its symmetrical position, it must not open at any pressure that may occur in the chamber when the pump is in this position, and always remain closed.

Displacement of the external valve from a symmetrical position, which is usually closed, to an inclined position in which the external valve can open and close, requires an external force in addition to the pressure in the chamber. Therefore, the proposed pump adds an additional requirement regarding the opening and dosing of the liquid to the requirement of a relative sufficient pressure in the chamber, which is the main one for the pumps of the prior art. In the proposed pump, an external force that causes the external valve to take an inclined position is the first requirement to open the external valve, and sufficient pressure in the chamber when the external valve is in the inclined position is the second requirement to open the external valve.

It is understood that the outer valve can theoretically open when in a symmetrical position. However, the external valve is usually easier to open when in an inclined position. Hereinafter, the term “opening pressure” is used to refer to the pressure difference between two compartments that are isolated by the valve at which the valve will open. Therefore, a valve having a higher opening pressure is more stable than a valve having a lower opening pressure.

The foregoing can be described as an external valve having an opening pressure in a symmetrical position when in a symmetrical position, and an opening pressure in an inclined position when in an inclined position, wherein the opening pressure in an inclined position is less than the opening pressure in a symmetrical position.

It is understood that the external valve, when in a symmetrical position in the chamber, will be symmetrically supported by the walls of the chamber. This usually leads to a relatively large opening pressure. This means that the valve seal in this position is relatively stable, which means that the pump will not inadvertently leak fluid.

In the inclined position, the symmetry is broken, and the external valve will asymmetrically contact the chamber walls during sealing. Such a seal will usually result in a lower opening pressure than a higher opening pressure obtained in a symmetrical position. Therefore, in this position, the valve will open more easily to allow fluid to flow from the chamber into the metering hole.

Therefore, the opening pressure in the symmetrical position can be selected regardless of the dosage of the liquid, but only taking into account the prevention of pump leakage. Therefore, a higher opening pressure can be selected, in addition to the prior art pumps, in which the external valve has only one position in which the opening pressure should not be higher than the opening pressure at which the fluid can still be dispensed through it. Therefore, in the proposed pump, the pressure in the chamber can be increased quite significantly without opening the external valve for dispensing liquid, until an external biasing force is applied. Therefore, an unintentional increase in pressure in the chamber, which may occur when the pump is controlled or as a result of a temperature difference in the environment, will not lead to the dosing of the fluid from the pump. The proposed pump is very leak resistant.

Preferably, the regulator comprises a rod supporting said outer valve, and in which the rod is resilient along its bend length, from the original shape in which the outer valve takes its symmetrical position to the curved shape in which the outer valve takes its inclined position. Thus, an external force can be applied to transfer the rod and its deformation, leading to the fact that the external valve assumes its inclined position regardless of the pressure present in the chamber.

Preferably, the stem is resilient to automatically return to a curved position after bending, causing the valve to automatically return to a symmetrical position from an inclined position. Essentially, relieving the external force will automatically cause the pump to return to the closed position.

Advantageously, the chamber is resilient to compress around the regulator, so that an external force compressing the chamber will be transmitted to the regulator, causing the external valve to take an inclined position. In this case, the compression of the chamber will transfer external force to the regulator to bias the external valve into an inclined position and at the same time increase the pressure in the chamber.

The above situation should not be excluded by the phrase "regardless of the pressure in the chamber" as used above. It is clear that also in this case, the displacement of the external valve is not caused by increased pressure in the chamber, but is caused due to the action of the chamber walls, which are shifted to the regulator.

In embodiments in which the regulator includes a bendable rod, as described above, it is understood that the biasing of the outer valve to an inclined position occurs in a direction opposite to the direction in which the increased pressure in the chamber acts to bias the outer valve.

However, since the compression of the chamber will cause the external valve to tilt and increase the pressure of the liquid contained in the chamber at the same time, it is understood that the pump will dispense the liquid as a result of the compression. Moving the pump to the metering position is caused by valve bias, and opening the external valve when in the metering position is caused by increased pressure in the chamber.

To further ensure the difference in opening pressures between the symmetrical position and the inclined position, the outer valve can advantageously be resilient and have a first flexibility through the first cross section, and this cross section is in contact with the camera when the outer valve is in a symmetrical position, and a second flexibility through the second a cross section, and this cross section is in contact with the camera when the outer valve is in an inclined position, the second flexibility being greater than the first bone, which leads to the fact that the said opening pressure in an inclined position is less than the said opening pressure in a symmetrical position.

Thus, the flexibility of the external valve can be used to achieve different opening pressures or increase different pressures, as already described, which are caused by different locations of the support from the walls of the chamber to the external valve. Flexibility can be controlled by varying the amount of material in different cross sections of the valve.

Advantageously, the outer valve has an outer shape at least partially repeating the contour of the ball, so that the first and second circular cross sections having the same radius corresponding to said symmetrical and inclined positions, respectively, can be determined.

In addition, a partially spherical valve has the advantage that it can be pressed into the chamber, providing relatively large contact surfaces between the valve and the chamber. This, in particular, takes place if the ball and / or chamber are made of elastic material. The relatively large surface contact provides a relatively large valve opening pressure.

Preferably, the peripheries of the first and second cross sections are of the same size and shape. Therefore, tight contact with a camera having a single cross-section at the location of the valve can be achieved in both symmetrical and inclined positions.

Advantageously, the maximum inclined position may be about 10-45 ° from the symmetrical position, preferably 20-30 °.

It should be understood that the inclined position is not a fully “open” position, i.e. the outer valve does not tilt to open. Instead, the tilted position is the position in which the valve acts as a pressure valve, opening and closing depending on ambient pressures.

To ensure that the outer valve does not open too much, i.e. to some extent, where tight contact with the chamber is no longer possible, a spacer element may be installed to prevent the valve from tilting beyond the maximum inclined position.

In the case where the controller comprises a bendable rod, the spacer element may advantageously be located on the rod to limit the bending movement of the rod. When the regulator is bent, the spacer element will as a result come into contact with the walls of the chamber, therefore, preventing further curvature of the regulator and setting limits also for tilting the external valve.

Preferably, the pump consists of only two parts, said casing and said regulator. It is understood that a pump in accordance with the foregoing can be performed using any number of parts. However, it is believed that a great advantage is that numerous advantages, as explained above, can be obtained using only two parts of the pump, housing and regulator.

In addition, the present application describes a dosing system comprising

- compressible container for liquid substance; and

- a pump connected with the possibility of compaction with a compressible tank, for supplying a liquid substance from the tank during its compression,

moreover, the pump contains

- a housing including a chamber and a metering hole, in which the pressure in the chamber can be changed for pumping fluid from the tank to the chamber and then from the chamber to the metering hole, and

a regulator located motionlessly in the chamber, for regulating the fluid flow between the container and the chamber and between the chamber and the metering hole,

in which the pump can take a closed position in which a volume of liquid is supplied from the tank to the chamber under the influence of the negative pressure created in the chamber, and a dispensing position in which the volume of liquid is supplied from the chamber to the metering hole,

in which the pump is made of plastic;

and the pump contains

- a return means automatically returning the pump from said dispensing position to said closed position, whereby the return means uses the elasticity of said plastic to overcome the negative pressure created in the compressible container during its emptying.

Therefore, in accordance with the present invention, the elasticity of the pump plastic is essentially used to effect the return of the pump from the dispensing position to the refilling position. This solution has a significant advantage over prior art systems, as it ensures that the return pump is made of plastic only.

Preferably, the return means has an initial shape corresponding to the closed position and a curved shape corresponding to the dosage position, wherein the return means is resilient to transition from the original shape to the curved shape under the action of an external force applied to the pump and automatically return to its original shape upon removal mentioned external effort.

Previously, it was not understood that the elasticity of the plastic may be sufficient to overcome the negative pressure created in the compressible container during its emptying.

Advantageously, the pump consists of a one-piece housing and one-piece regulator, therefore, only two parts. The use of several parts is advantageous in connection with the savings in the manufacture and assembly of parts, and contributes to the operational reliability of the pump.

The plastics used in the pump need not be the same, but preferably should be of the same type, so that the pump can be disposed of as a single device. In addition, the compressible bottle should preferably be made of plastic, like a pump, so that the entire system can be disposed of as a single device. This is especially advantageous, since in this case, people who are monitoring the emptying of the systems can avoid the trouble caused by the leakage of residual liquid from the tank or pump. As will be understood from the following description of detailed embodiments, the proposed system can be designed such that the pump maintains a compacted state even when the bottle is empty. Such embodiments will undoubtedly be especially easy to handle after use.

Advantageously, the container is a semi-rigid compressible container. By “semi-rigid” is meant a container, as mentioned in the introduction, which contains at least one relatively rigid section to which compression of other less rigid sections will be directed. This type of compressible containers is advantageous in that information can be printed on a hard area, and the information remains clearly visible and undistorted regardless of the compression state of the container. In addition, for some contents, containers containing at least one relatively rigid wall can preferably be used instead of bags. However, compressible containers containing at least one relatively rigid wall may require a greater suction force generated by the pump to overcome the negative pressure created in the vessel during emptying, as compared to bags. A particular advantage in the case of the proposed system is that it can be implemented to effectively overcome the relatively large negative pressure created also by semi-rigid compressible containers.

Most preferably, the system comprises a container containing one rigid longitudinal half and one compressible longitudinal half, so that during emptying, the compressible longitudinal half will fit snugly against the compressible longitudinal half. This type of container is suitable for installation in many existing metering systems to meet the visibility requirements of information printed on the container. In addition, a concrete form with a half compressible to the other half ensures that empty containers require especially little space.

Advantageously, the chamber is resilient for compression from the original shape corresponding to the system in the closed position to the compressed curved shape corresponding to the system in the dosing position, and wherein the camera automatically returns to its original shape after compression, as a result of which the camera forms part mentioned means of return. It is clear that due to this device, when removing an external force compressing the camera, the camera tends to return to its original shape. Returning to its original shape means that the chamber is stretched, which creates negative pressure in the chamber. The negative pressure created in this way will be effective for refilling the chamber.

Advantageously, the chamber is usually cylindrical.

Advantageously, the regulator is flexible along its length for bending after external force is applied to the pump from the initial form corresponding to the system in the closed position to the curved form corresponding to the system in the dispensing position, and the controller automatically returns to its original form when removal of external force, as a result of which the regulator forms part of the said return means. When the external force causing the controller to bend is removed, the controller will tend to return to its original position corresponding to the closed position of the pump.

Advantageously, the regulator is located inside the chamber, so that the external force compressing the chamber will simultaneously lead to the bend of the regulator, setting the pump in the dosing position, and when external force is applied, the chamber and regulator will automatically return to their original shapes, setting the pump in the closed position. This installation is particularly suitable as it provides relative tightness of the practical embodiments against leakage.

Preferably, the regulator comprises a rod and at least one valve, where the regulator is resilient along the length of the rod.

Preferably, the regulator comprises a rod and at least one valve, where the regulator is resilient along the length of the rod.

Advantageously, the controller comprises a shaft and an external valve, wherein the external valve is arranged to regulate the fluid flow between the chamber and the metering hole when the controller takes its initial shape, the external valve is in a symmetrical position in the chamber corresponding to the closed position of the pump when the controller takes its curved shape , the external valve is in an inclined position in the chamber corresponding to the dosing position of the pump.

In this embodiment, the elasticity of the regulator is used to bias the external valve, so that the valve has a symmetrical position in the chamber when the pump is in the closed position, and an inclined position in the chamber when the pump is in the dispensing position.

Brief Description of the Drawings

The present invention will be further described as an example implementation with reference to the accompanying drawings, in which:

figa-1d schematically depict a dosing / refilling cycle of an embodiment of a pump in accordance with the present invention;

figa-2c depict the regulator of the embodiment of figure 1;

figa-3c depict the housing of the embodiment of figure 1;

figa-4c depict an embodiment of a connector for use with the pump of figure 1;

figa and 5b depict the assembly of the regulator on figa-2c, the housing on figa-3c and the connector on figa-4c.

figa-6c depict a system containing a compressible container and Assembly in figa and 5b.

Similar reference numerals are used to indicate like elements throughout the drawings.

Detailed Description of Preferred Embodiments

1a-1d schematically depict one dosing / refilling cycle of an embodiment of a pump 1 in accordance with the present invention. To simplify figa-1d were removed some of the elements that can be dispensed with when explaining the basic functions of the pump. Instead, the specific elements of the illustrated embodiment are explained with respect to other drawings and in connection with further advantages of the present invention.

In use, the pump 1 must be hermetically connected to a container containing a liquid substance, such as liquid soap or alcohol detergent. The capacity is schematically indicated by reference numeral 400 in FIGS. 1a-1d. The pump 1 comprises a housing 100 and a regulator 200 fixedly located in the housing 100. The housing 100 forms a chamber 110 in which, as will be described below, the pressure can be changed to dispense the liquid from the pump 1 or to refill the liquid from the compressible container 300. In addition, the housing 100 comprises a dispensing opening 120 through which said liquid can be dispensed.

A controller 200 is fixedly located in the chamber 100 to control the flow of fluid between the container 400 and the chamber 110 and between the chamber 110 and the metering opening. In the illustrated embodiment, the controller 200 comprises an external valve 220, which, as shown in FIG. 1a, is in close contact with the chamber 110, and which controls the flow of fluid between the metering opening 120 and the chamber 110.

The regulator also includes an internal valve 230, which, as shown in Fig. 1a, is also in close contact with the chamber 110, and which regulates the flow of fluid between the compressible reservoir 300 and the chamber 110. In addition, the regulator 200 may advantageously comprise locking means for performing fixing the controller 200 in the chamber 100. In this embodiment, the locking means comprises a locking plate 250.

In this application, the term “internal” or “inside” is usually used to refer upstream to the container and in the opposite direction to the dosing, while the term “external” or “outside” is usually used to point downstream to the outlet and in the direction of dosing.

Dosing position

Fig. 1a shows a pump when it is in the closed position. In this application, the term “closed position” is used for a position in which the flow does not pass between the chamber 110 and the outlet 120. In FIG. 1a, the pump is in the closed position, which is also a storage position in which the flows do not pass in the system. That is, the regulator 200 controls the flow, so that the fluid flow does not pass between the container 300 and the chamber 110 or the chamber 110 and the outlet 120. In the illustrated embodiment, the outer valve 220 and the inner valve 230 are closed and are in tight contact with the chamber 110 (i.e. e. with the inner walls of the chamber 110). During use, chamber 110 will fill with liquid when the pump is in the storage position.

Fig.1b depicts a pump while in the dispensing position. In this application, the term "dispensing position" is used for a position in which a volume of liquid can be sucked from the chamber 110 into the dispensing opening 120. In the dispensing position, the outer valve 220 is set in an inclined position by an external force transmitted to the controller 200.

The opening pressure of the external valve in the inclined position is less than the opening pressure of the external valve in the initial, symmetrical position, i.e. the external valve opens more easily when in an inclined position compared to a symmetrical position. This can be explained by the external valve 220 when in a symmetrical position, supported symmetrically around its periphery by the walls of the chamber 110. This increases the resistance of the valve against compression. In the inclined position, this symmetry is broken. On one side of the outer valve 220, the chamber wall will be in contact with the valve 220 in a position closer to its center than in the symmetrical position, and on the other side of the outer valve 220, the chamber wall will be in contact in a position farther from the center of the valve than in the symmetrical position. Therefore, the “blocking” effect achieved by symmetrical forces is no longer present, which means that the opening pressure in the inclined position is less than the opening pressure in the symmetrical position.

In addition, in the illustrated embodiment, the outer valve 220 is configured so that its flexibility through the section of the valve 220, which comes into tight contact with the wall of the chamber 110 in the symmetrical position (Fig. 1a), is less than the flexibility through the section of the valve, which is in tight contact with the wall of the chamber 110 in an inclined position (fig.1b). When the flexibility of the effective tight contact portion of the outer valve 220 increases, the opening pressure will decrease. A more detailed description of this embodiment of the outer valve 220 will be given later in this application.

It is understood that in the symmetrical position corresponding to the closed position of the pump, the opening pressure of the external valve 220 can be selected so that it can withstand a slight increase in pressure in the chamber 110 without opening. Only if the outer valve 220 is tilted, which requires an external force to be applied to the pump, the outer valve 220 can open to dispense fluid from the chamber 110.

The outer valve 220 is also designed to perform the function of a pressure-controlled valve while in an inclined position. In other words, the outer valve 220 will not tilt to partially move away from the wall of the chamber 110 and, therefore, to open by tilting only. Instead, if there is no pressure drop or there is only a small pressure drop between the chamber and the metering orifice, the outer valve 220 should seal between them also when it is in its inclined position.

In the illustrated embodiment, the chamber 110 is resilient to contract when an external force is applied, as shown by the arrow in FIG. 1b. Compression of chamber 110 will cause an increase in pressure in the fluid contained therein.

In addition, in the illustrated embodiment, the regulator 200 is resilient along its length to bend from a neutral position, as shown in FIG. 1a, to a curved position, as shown in FIG. 1b. When the regulator is in its bent position, the outer valve 220 takes an inclined position in the chamber 110.

In the illustrated embodiment, the controller 100 comprises a spacer 240 to ensure that the outer valve 220 tilts too far. The spacer 240 is located on the inner side of the stem of the outer valve 220 and will come into contact with the inner wall of the chamber 110 during bending of the stem. Essentially, it limits the bending of the rod and prevents the tilt of the outer valve 220 beyond the maximum tilt position.

The illustrated embodiment is particularly advantageous in that the external force performs both compression of the chamber 110, resulting in increased pressure in the chamber 110, and bending of the regulator 200, resulting in reduced opening pressure of the outer valve 220, which cooperate to open the outer valve 220, so that the liquid will be squeezed out of the chamber 110 to the dispensing hole 120.

In addition, externally, the force compressing the chamber 110 will simultaneously cause the controller 200 to bend, setting the pump in the dispensing position.

In the above description, the basic principle of operation of a pump comprising an external valve displaced from a closed position to a dispensing position has been described with reference to FIGS. 1a and 1b. It should be understood that other embodiments may be provided that will use this basic principle of action. For example, although less predominantly, one can imagine the use of a regulator 200, only a part of which will be made elastic, or a regulator 200, consisting of a number of parts, of which only one is elastic to effect the biasing of the external valve. In addition, if a rigid chamber 110 is used, some other means, such as a separate piston, can be used to bias the external valve, and optionally also to increase the pressure in the chamber.

Automatic return mechanism

Description of the illustrated embodiment will be continued with specific reference to FIGS. 1b and 1d.

In the illustrated embodiment, the chamber 110 and the regulator 200 are made of elastic materials, preferably plastics. In the dispensing position, as shown in FIG. 1b, both the chamber 110 and the regulator 200 are bent with respect to their original shapes, as seen in FIG. 1a. Upon removal of the shock load, the chamber 110 and the regulator 200 will automatically return to their original forms and, therefore, return to the closed position, as shown, for example, in Fig. 1d.

After dispensing the liquid, when the external force is removed, the chamber 110 returns to its original shape and, therefore, expands. The regulator 200 returns to its original shape, causing the outer valve 200 to return to its symmetrical shape, closing the chamber 110. The expansion of the chamber 110 creates a negative pressure in the chamber 110, which will cause the opening of the inner valve 230, as shown in fig.1d. Therefore, liquid will be supplied from the container 300 to the chamber 110 to fill the chamber 100. When the chamber is refilled, negative pressure will not be present in the chamber 110, and the internal valve 230 will close again, returning the pump to its initial position in FIG. 1a.

In the above description and in the following description, it should be understood that the pump in the closed position refers to the pump closed in such a way that the liquid cannot pass through the metering opening 120. The outer valve 220 is in its closed, symmetrical position. However, in the closed position, the internal valve 230 may open to refill the chamber 110 with liquid from the container. Therefore, FIG. 1d depicts the closed position of the pump, which is also the refill position.

In the illustrated embodiment, the automatic return of the pump 1 from the dispensing position to the closed position is performed by the controller 200 and the chamber 110, which return to their original shape after they are bent. Therefore, in this embodiment, both the regulator 200 and the chamber 110 form a return means made of the material of the pump parts.

Therefore, in the aforementioned description, the basic principle of operation of a pump comprising a return means made of resilient plastic of the pump and using said elasticity to provide automatic return of the pump has been described with reference to FIGS. 1a and 1d. In addition, the return means is sufficient to overcome the negative pressure created in the compressible container. It should be understood that other embodiments may be considered that will use this basic principle of action. For example, although it is believed that this is less advantageous, it can be imagined that only one of the controller or camera forms a return means. In addition, the return function does not have to be combined with a tiltable external valve (although this is believed to be particularly advantageous).

Liquid back suction device

The foregoing description of the illustrated embodiment with reference only to FIGS. 1a, 1b and 1d describes, in essence, a possible dosing / refilling cycle of the pump. However, this description is somewhat simplified. In the following, the basic principle of the operation of the device for the reverse suction of a liquid for a pump for a metering system for liquids will be described with specific reference to figs.

The illustrated embodiment, which was used above to illustrate the principle of the pump, is also suitable for describing the basic principle of the operation of the reverse suction device. However, it should be understood that the liquid back suction device may also be used in other contexts than in this particular embodiment.

The liquid back suction device is based on the presence of an internal valve 230, which is a one-way valve, for opening the liquid flow in the dispensing direction at the opening pressure of the internal valve acting in the dispensing direction and closing at any pressure acting in the direction opposite to the dispensing direction, and an external valve 220, which is a two-way valve, to open for fluid flow in the metering direction or in the opposite direction to the metering pressure at the opening pressure of the external valve, depending on the direction of the opening pressure of the external valve.

In the illustrated embodiment, the inner valve 230 is typically a parabolic valve cooperating with a seat 130 formed from the inner wall of the housing 100. The seat 130 is located upstream of the internal valve 230, so that the internal valve 230 will act as a one-way valve, opening in the direction dosing.

In the illustrated embodiment, the outer valve 220 is a partially spherical valve that interacts with the inner walls of the housing 100. When in its tilted position, the outer valve 220 will act as a two-way valve, opening to flow in the direction of the pressure gradient between the chamber 110 and the metering orifice 120.

When the pump is in the dispensing position, as shown in FIG. 1b, the pressure in chamber 110 is greater than the pressure in the dispensing orifice 120, and the outer valve 220 will open to allow fluid to flow from the chamber 110 to the orifice 120.

After dispensing fluid from the chamber 110, the pump will move from the dispensing position in FIG. 1b to the closed position in FIG. 1d, in which the outer valve 220 will return to its symmetrical position and negative pressure will be generated in the chamber 110.

However, the property of the two-way valve of the outer valve 220 becomes effective during a short transition period during which the pump moves from the dispensing position (Fig. 1b) to the closed position (Fig. 1d), as shown in Fig. 1c. When external pressure is released to the chamber, negative pressure will immediately arise in chamber 110. However, the return of the external valve 220 from its inclined position to its symmetrical position does not occur as quickly as the occurrence of negative pressure. Therefore, for a short period of time, the outer valve 220 remains in an inclined position, and at the same time a negative pressure occurs in the chamber 110.

A negative pressure in chamber 110 will cause the external valve 220 to open to allow the remaining liquid and / or air to pass from the metering port to the chamber 110. At the same time, the internal valve 110 will open to allow fluid to flow from the container 300 to the chamber 110. Therefore, as shown by arrows on figs, in this situation, one fluid flow in the dispensing direction passes into the chamber 110 through the internal valve 230, and one fluid and / or air flow in the opposite direction of the dispensing flow in chamber 110 through an external valve 220.

However, the outer valve 220 will ultimately return to its symmetrical position, as shown in FIG. 1d. In this position, the opening pressure of the external valve is greater than the opening pressure in the inclined position, and the valve will no longer open to flow in the opposite direction to the metering direction. In contrast, the internal valve 230 remains open until the chamber 110 is refilled with liquid.

Therefore, any liquid remaining in the dispensing opening 120 of the housing 100 after the dispensing position can be sucked back into the chamber 110 as the pump moves from its dispensing position to its closed position. The reverse suction should be limited, since it is necessary that the chamber is filled with liquid from the container 300, and not with air through the metering hole 120. In accordance with the presented principle of reverse suction of the liquid, this is ensured due to the fact that the reverse suction of the liquid occurs only during the movement of the pump from the dispensing position to its closed position, and the bulk of the refilling of the chamber 110 is performed in the closed position.

In addition, the opening pressure of the internal valve should preferably be less than the opening pressure of the external valve, so that the external valve will close before the internal valve, since the negative pressure in the chamber is equalized.

In the foregoing description, the basic principle of operation of a liquid back suction device using a two-way external valve and a single-acting external valve has been described with reference to FIG. 1c. However, although this is less advantageous than the illustrated embodiment, it is believed that other embodiments using this basic principle may be implemented. For example, other types of one-way valve and two-way valve may be provided. In addition, it is believed that the device for the reverse suction of the liquid does not have to be combined with an automatic means of returning from elastic materials, but can also be presented in embodiments where an external force is necessary to return the system to the closed position.

From the foregoing description, at least three basic principles can be distinguished. Firstly, the external valve is shifted between the symmetrical position and the inclined position when the pump moves from the closed position to the metering position. This feature, in particular, provides a pump design that does not have leakage problems. Secondly, the pump is automatically returned to the closed position from the dosing position, in which the elasticity of the plastics of the pump is used. This feature provides, in particular, simple and recyclable structures that are nonetheless resistant to overcome the negative pressure created in the compressible container. Thirdly, there is a liquid back suction device that uses a single-acting internal valve and a two-way external valve and is activated when the pump moves from the dispensing position to the closed position.

It is understood that the illustrated embodiment is particularly advantageous since it combines all three basic principles in a simple design. Nevertheless, it is believed that these three principles can be used separately, if only one of the specific advantages associated with them is needed.

Other preferred elements

In the following, further advantageous elements of the illustrated embodiment will be described.

REGULATOR

2a-2c depict a controller for an illustrated embodiment. Fig.2a is a perspective view of the regulator, Fig.2b is a sectional view of the regulator, and Fig.2c is a view of the regulator when viewed from the extreme end inward.

External valve

As can be seen in FIGS. 2a and 2b, the outer valve 220 has an outer shape, partially repeating the contour of the ball. As best seen in enlarged portion A in FIG. 2b, the ball extends from the attachment portion to the shaft along a curve forming an edge 222.

The edge 222 is flexible toward the center of the valve 220 and resilient to return its original handicap after folding. The flexibility of the edge 222 is advantageously provided by the edge having a substantially constant thickness. In the center of the outer valve 220, surrounded by an edge 222, there is a bulge 224. The bulge 224 and the stem material will stiffen the valve 220. Furthermore, the bulge 224 is particularly effective when the pump is used to pump out high viscosity fluids, which will be described later.

On the enlarged part A, it is seen that the edge 222 forms a straight section 226 just before the completion of the relatively short end section 228, which bends inward to the center of the valve 220. However, it is clear that it has a shape that is basically (although not necessarily exactly) repeating outer contour of the ball. The expression "spherical" is given in this context for the concept in contrast to, for example, the conical or parabolic shape of the valve.

It is understood that when the outer valve 220 is in its symmetrical position in chamber 110, the straight portion will be in contact with the walls of the housing. However, an embodiment may be suggested in which the straight portion 226 is replaced by a portion extending, repeating an exact spherical contour. In addition, such a section may be in contact with the walls of the chamber when in a symmetrical position, but, however, it will be possible to straighten somewhat under the action of the walls of the chamber.

This is believed to be advantageous if the outline of the outer valve forms a surface portion that can remain parallel to the inner surfaces of the chamber 110 at the same time. With this design, the surface portion of the outer valve can be inserted into the chamber 110 so that its walls exert a symmetrical pressure on the valve surface portion . The clearance between the outer valve 220 and the chamber 110 may be selected to provide a relatively relatively open pressure when the outer valve 220 is in its symmetrical position, where the pressure between the parallel walls of the chamber and the parallel surface portions will provide the opening pressure of the outer valve.

The inwardly curved portion 228 of the illustrated outer valve 220 is suitable for facilitating movement between the tilted position and the symmetrical position of the valve 220. In addition, it provides the function of backward suction of the liquid, since it contains a surface that can be acted upon by pressure in the metering opening of the valve to open external valve in the opposite direction to the metering direction of the pump.

It is understood that the outer valve 220, when located in the chamber 110, is compressed peripherally to perform a sealing function. Therefore, in a relaxed, uncompressed state, the outer valve 220 has an outer diameter that is larger than the diameter of the chamber 110 at the location of the outer valve 220. As can be seen in FIG. 5b, in the illustrated embodiment, the regulator of the outer valve 220 will be located in the outer compartment 112 of the chamber.

Advantageously, the difference between the inner diameter of the chamber at the location of the outer valve 220 and the outer diameter of the outer valve 220 when uncompressed is 0.09-0.20 mm, preferably 0.10-0.20 mm, most preferably 0.10-0 , 15 mm.

In the illustrated embodiment, the difference between the inner diameter of the chamber at the location of the outer valve 220 and the outer diameter of the outer valve 220 when in an uncompressed state is about 0.15 mm.

Spacer element

Next to the outer valve 220, there is a spacer member 240 that performs the function of adjusting the tilt of the outer valve 220, which has been described above. The outer shape of the spacer element 240 can be easily determined with respect to the outer valve 220 and the shape of the chamber 110 to perform its function. In the illustrated embodiment, the spacer 240 comprises recesses 242, some longitudinal, some transverse. The recesses 242 facilitate the passage of fluid through the spacer element 240. In addition, this element is particularly suitable when the pump is used to pump out high viscosity fluids, as will be described below.

Kernel

The shaft 210 typically extends between the internal valve 230 and the external valve 220. The shaft is resilient to provide folding and is able to return to its original shape after folding. The length and diameter of the shaft 210 can be selected taking into account these factors, as well as others regarding, for example, the size of the pump. In the illustrated embodiment, the diameter of the rod is about 3 mm, and the length of the entire regulator is about 55 mm. In the illustrated embodiment, the rod 210 has a constant diameter.

Guide element

A guide member 260 is located adjacent to the top valve 230 on its outer side. The guide member 260 extends laterally to limit the bending movement of the shaft 210 and typically limits bending in a portion of the shaft 210 extending to the outside of the guide member 260. Essentially, the guide member 260 is effective in ensuring that the function of the inner valve 230 is not affected by the bending movement of the shaft 210. The guide member 260 can advantageously extend around the periphery and a rod 210 for symmetrically restricting the movement of the rod. In the illustrated embodiment, the guide member 260 is formed of four guide rods 262 arranged to intersect with the shaft 210 in its center.

Internal valve

The inner valve 230 comprises a valve extending circumferentially from the stem 210. The width of the valve is usually constant from the position in which the valve extends from the stem 210 and to its outer end. In the illustrated embodiment, the shape of the valve can be described as basically forming the shape of a parabola. However, as can be seen in enlarged part B, the valve does not exactly repeat the parabolic contour. Rather, the valve forms a series of more straightforward sections, which, when viewed as a whole, can usually be taken as the contour of a parabola.

The inner surface of the valve is connected to the stiffener 234. The stiffener 234 is stiffer than the valve and performs the function of restricting the movement of the valve. Advantageously, the stiffener 234 is attached to the upper surface of the valve at a number of mounting locations. At these locations, a stiffener 234 rigidly connects the valve to the stem 210. Consequently, the valve is fixed at the attachment locations and prevented from moving outward or inward at these locations.

By preventing inward movement, the stiffening element 234 ensures that the valve cannot twist in the wrong direction, i.e. in the opposite direction to the dosing direction, even if the pressure in chamber 110 must be higher than the pressure in the vessel 300 to which the pump is connected. This element is particularly effective when the pump is used to empty the compressible tank 300. In the compressible tank 300 and, in particular, in the compressible tank 300, which is semi-rigid, negative pressure can be created in the tank when fluid is supplied from it by the pump. Therefore, when the pump is in the closed position and the chamber 110 is filled with dosing liquid in the next dosing cycle, the pressure in the chamber 110 may be higher than the pressure in the vessel 300. In addition, the pressure gradient between the chamber 110 and the vessel 300 can be relatively large. The stiffener 234 contributes to an internal valve 230, which is a robust one-way valve that can withstand relatively large pressure gradients in the opposite direction to the metering direction without opening.

By preventing outward movement, the stiffener 234 helps control the opening of the internal valve 230.

In the illustrated embodiment, the stiffener 234 comprises four protrusions extending from the shaft 210 and forming an intersection with the shaft 210 in the middle. The protrusions are connected to the valve at attachment locations along the outside of the protrusions.

It is understood that stiffener 234 should not impede the movement of the entire valve. Some sections of the valve must remain movable for possible opening and closing. This can be achieved due to the mounting locations between the stiffener 234 and the valve, limited by the internal area of the valve, leaving the edge 232 without being attached to the stiffener 234 and passing around the periphery of the valve. Alternatively, or in combination with an edge 234, portions of the valve extending between spaced apart mounting locations of the stiffener 234 may be movable to open and close the valve. However, in particular, for use with a compressible container in which negative pressure can be generated, as described above, it is preferable that an edge 232 is formed, so that the ability of the stiffeners 234 to prevent the back opening of the internal valve 230 need not be used to open the valve in the right direction.

In the illustrated embodiment, an edge 232 is formed without being connected to a stiffener 234 that extends around the periphery of the valve. It is believed that the shape of this lip 232 is more important for the valve sealing function than the shape of the inner portions of the valve, which are, however, substantially blocked from movement by the stiffener 234.

Edge 232 will contact the housing 100 when in the closed position, and will move from the housing 100 in the open position. As can be seen in fig.5b, the edge 232 can mainly interact with the ledge 119 formed in the wall of the chamber. Therefore, the re-opening of the valve 230 at the edge 232 is prevented by the presence of the step 119.

The edge 232 forms an angle α with the longitudinal center of the regulator 200 (i.e., with the shaft 210). Preferably, the angle α is in the range of 15-30 degrees, more preferably 20-30 degrees, most preferably 20-25 degrees. In the illustrated embodiment, the angle α is about 23 degrees.

The thickness of the flange 232 should be selected depending on the elastic plastic, so that the flexibility of the flange 232 allows the opening and closing of the internal valve. This is believed to be an advantage, taking into account the resilience, if the thickness of the edge 232 is substantially constant over the entire length of the edge 232. Preferably, the thickness may be from 0.2 to 0.4 mm. In the illustrated embodiment, the edge thickness is about 0.3 mm.

In view of the foregoing, it is contemplated that the entire internal valve 232 may be formed in other conventional forms as opposed to a parabolic form. For example, the internal valve may have a conventional conical shape. Typically, the shape of the portions that are prevented from being moved by the stiffening element 234 can be freely selected since they will not move. However, this is believed to be advantageous since the valve edge 232 has properties as described above.

It is generally understood that the internal valve 230 may provide a seal to the entire system, consisting of a compressible reservoir in a fluid tight connection to the pump. The internal valve 230 must be a one-way stable valve, opening only in the metering direction and at the opening pressure of the internal valve. Since negative pressure is created in the vessel, only a higher negative pressure in the chamber can cause the opening of the internal valve. Negative pressure in the chamber is created only immediately after dosing the liquid, when the chamber 110 must be re-filled. In all other situations, in particular in a situation where the pump is not used, and the chamber must be closed and filled with liquid, negative pressure and a higher pressure in the chamber occur in the bottle. Therefore, the internal valve 230 will reliably isolate the container from the chamber. This means that in this situation, the external valve 220 should only ensure that the contents of the chamber do not leak, i.e. external valve 220 should not support the weight of the contents of the container.

It is understood that the internal valve 230, when located in the chamber 110, is compressed peripherally. Therefore, in a relaxed, uncompressed state, the inner valve 230 has an outer diameter larger than the diameter of the chamber 110 at the location of the inner valve 230. As can be seen in FIG. 5b, in the illustrated embodiment, the inner valve 220 will be located on the upper portion of the middle housing section 114.

Advantageously, the difference between the inner diameter of the chamber at the location of the inner valve 230 and the outer diameter of the inner valve 230 in an uncompressed state is 0.20-0.35 mm, preferably 0.25-0.35 mm, most preferably 0.25-0 , 30 mm.

In the illustrated embodiment, the difference between the inner diameter of the chamber at the location of the inner valve 230 and the outer diameter of the inner valve 230 in an uncompressed state is about 0.3 mm.

Fixing plate

The controller 200 further comprises locking means for fixing the controller 200 in the housing 100. In the illustrated embodiment, the locking means comprises a locking plate 250 located on the shaft 210. Advantageously, the locking plate 250 is located, as shown, at the extreme end inward. The locking plate 250 is a circular plate that should be inserted into the corresponding protrusion at the extreme portion in the direction inward of the housing 100. The plate 250 contains apertures 252 for flow to ensure the passage of fluid flow from the tank 300 to the pump. The size and shape of the flow openings 252 may be selected to control the volume of flow from the reservoir 300 to the pump. For example, flow openings 252 may be formed as slots extending from the edge of the fixing plate 250 to its center.

In the illustrated embodiment, three circular flow openings 252 are formed in the fixing plate 250. If the pump is to be used to pump liquids with relatively high viscosities, this is considered to be an advantage in forming flow openings 252 with a larger cross-sectional area than the openings of the illustrated embodiment implementation. For liquids with high viscosity, two relatively large slots can be formed opposite each other. By adjusting the size of the slots, fluid flow can be controlled. For example, two slots can occupy almost half the surface of the retainer plate 250, with each slot including about a quarter of a circle.

HOUSING

Figa-3c depict the housing of an example implementation. Fig. 3a is a perspective view of the housing, Fig. 3b is a sectional view of the housing, and Fig. 3c is a view of the regulator when viewed from the farthest end.

The housing 100 is typically cylindrical, extending from an inwardly extending portion containing a receptacle 140 for connection to the receptacle to a remotest portion including a dispensing opening 120.

Closure

As can be seen in FIGS. 3a and 3b, the housing 100 may, in its initial position, comprise a closure 130 for sealing the metering opening 120. The closure 130 must be removed during operation of the pump. The closure 130 will ensure the integrity of the pump during, for example, transportation and storage, so that contaminants will not enter the housing 100 through the metering opening 120. In the illustrated embodiment, the closure 130 is integrally formed with the housing 100. The closure 130 comprises the upper part, which is connected to the housing surrounding the dispensing hole 120, using a softening line 132. The thickness of the housing material is reduced along the softening line, so that the closure means 130 can be removed by pulling or twisting the upper part, causing a break in the softening line 132.

Taking into account the manufacture, as well as reliability, the most advantageous is the implementation of the closure 130 as a whole with the body, an example of which is shown in the illustrated embodiment. However, of course, other less preferred closures are possible, for example a cover tape or a separate cover stopper.

Outdoor office

The outermost portion of the housing forms the outer compartment 112. As can be seen in FIG. 5b, the outer valve 220 will be enclosed in the outer compartment 112 in the assembled pump.

Therefore, the inner diameter of the outer compartment 112 and the outer diameter of the outer valve 220 must be configured to provide a given sealing effect. To this end, the outer diameter of the outer valve 220 is usually slightly larger than the inner diameter of the outer compartment 112, so that the outer valve 220 is slightly compressed when in place in the outer compartment, causing the inner wall of the outer compartment 112 to press on the outer valve 220. The difference in size between the outer compartment 112 and the outer valve 220 may be selected taking into account the elasticity and flexibility of the outer valve 220 to provide a sufficiently strong seal of the outer valve 220. However, it should be understood that the spacing s size in question in this context, a small, possibly in the range of 1-2%, which in the illustrated embodiment corresponds to 0.15 mm.

When the housing is made of elastic material, as in the illustrated embodiment, it is usually necessary that the shape of the housing around the outer compartment 112 is relatively stable, since otherwise the function of the outer valve 220 that is contained therein may be impaired. Therefore, in the illustrated embodiment, the thickness of the walls of the housing surrounding the outer compartment 112 is relatively large.

Flow control tool

The end portion of the outer compartment 112, on which the dispensing hole 120 is formed, comprises flow control means 138. The flow control means 138 is configured to provide the corresponding function of the pump 1 also when pumping liquids having a relatively high viscosity.

As was briefly mentioned above, high viscosity fluids will define specific pump requirements. Since the shaft 210 is resilient, it can bend not only in the transverse direction when bent, but it can also lengthen. This can happen when the pump is used to pump high viscosity liquids. High-pressure fluid pressure can cause elongation of the stem 210 when the outer valve 220 is in its symmetrical position in the outer compartment 112, so that the outer valve 220 is pushed out toward the end of the housing 100, although it is still in a symmetrical position in the housing. If there were no flow control means 138, there would be a possibility that the outer valve 220 would come into contact with the bottom of the outer compartment 112 containing the dispensing hole 120, a situation that could impair the function of the outer valve 220.

In order to provide the function of the external valve 220, when the shaft 210 is in the elongated position, the flow control means 138 is configured to eliminate the contact of the external valve 220 with the dispensing hole 120 and the end wall of the housing 100. Therefore, the flow control means 138 usually consists of intermediate elements that distributed around the metering opening 120, and which form a stop for the outer valve 220.

In the illustrated embodiment, the flow control means 138 comprises a circular protrusion 134 surrounding the dispensing opening 120. A plurality of grooves 136 are provided on the protrusion 134 to allow fluid to flow through the dispensing opening 120 when the outer valve 220 contacts the protrusion 134. In this particular embodiment, four grooves extending from the metering hole 120 through the protrusion 234 and forming an intersection with the metering hole in its center. As mentioned above, the outer valve 220 of the illustrated embodiment comprises a central bulge 224. When the outer valve 220 is in contact with the protrusion 134, this bulge 224 will rest on the protrusion 134. The edge 222 of the outer valve 220 may extend around the protrusion 134 so that it the compaction function is not exposed to contact with the flow control means 138. From this position, the outer valve 220 can be tilted and opened to dispense fluid, as described above. The liquid will exit through the dispensing opening through the grooves 136 in the protrusion 134. In addition, any backward suction of the liquid can occur through the grooves 136.

In view of the foregoing, it is understood that the flow control means 138 may be located at the end of the outer compartment 112 to interact with some central external valve support means 224, so that if the regulator 200 is extended, for example, when a high viscosity fluid is pumped out, the central support means can contact the flow control means while providing the function of the external valve 220. This can be achieved by convexity 224 of the external valve 220 in contact with the control means eniya stream, while ensuring passage of the edge 222 of the outer valve 220 around the flow control means so that its function is not impaired.

When the regulator 200 is in an extended position, the spacer element 240 can move forward, so that it at least partially enters the outer compartment 112. As can be seen in FIG. 5b, the spacer element 240 can also be configured to limit the elongation of the regulator 200 by arranging expansion elements that cannot enter the outer compartment 112. The recesses 242 on the spacer 240 become effective to facilitate the passage of fluid through the spacer 240 if the spacer is at least the partially inserted into the relatively narrow outer compartment 112.

Incline

At the extreme end directed inward of the outer compartment 112, the inner diameter of the housing 100 expands to form a middle compartment 114. The middle compartment 114 will typically contain a certain amount of dosed liquid. Therefore, the size of the middle compartment 114 should be selected in accordance with the specified maximum dosed volume.

In the illustrated embodiment, the inner diameter of the middle compartment 114 is wider than the inner diameter of the outer compartment. The diameter does not expand sharply, but gradually increases along part of the length of the housing to form an inclination 118. The inclination 118 is effective in that it provides a fluid flow through the housing 100. In addition, the inclination 118 can come into contact with the spacer 240 of the regulator 200 for regulation the slope of the regulator 200. By adjusting the contour of the slope 118 and the contour of the spacer 240, it is possible to adjust the bend of the regulator, in particular as mentioned above, so that the slope of the outer valve 220 is limited.

Ledge

At the extreme end, toward the inside of the middle compartment, the inner wall of the housing 100 forms a step 119 to form a saddle of the inner valve 130. Therefore, the inner diameter of the housing 100 narrows to form a saddle, which the inner valve 130 can abut in the opposite direction to the metering direction. The size and shape of the shoulder should be adapted to the internal valve 130 to form a reliable one-way valve, as described above.

In particular, when the inner valve 130 comprises a stiffener 234 and an edge 232, it is understood that the step 119 must be made to form a support for the edge 232. Therefore, it can be said that the stiffener 234 and the step 119 are complementary, both of which prevent the opening of the inner valve 130 in the wrong direction.

It is understood that without the stiffening element 234, and in particular if a relatively flexible inner valve 134 is used, there may be a risk that the internal valve is deformed so that the edge 232 slides off the step 119 and the valve 134 opens in the opposite direction dosing. Therefore, the stiffener 234 is particularly effective when using relatively flexible valves.

Interior office

Inside the ledge 119, the housing 100 forms an inner compartment 116. The inner compartment 116 will accommodate a stiffener 234 and fixation means between the regulator 200 and the housing 100. In the illustrated embodiment, the regulator retainer plate 250 is secured in a corresponding retaining groove 117 on the inner wall of the inner compartment 116.

Body wall

Typically, the wall thickness of the housing is appropriate to provide the desired elasticity of the chamber 100. It will be appreciated that in the illustrated embodiment, the chamber 110 is substantially constituted by the middle compartment 114 of the housing 100. Therefore, the wall thickness of the housing is relatively thin in the middle compartment 114 to compress the chamber 100 The wall thickness of the casing around the outer compartment 112 and the inner compartment 116 is relatively large, so that the shape of the casing is kept more constant for these compartments 112, 116. This provides the corresponding function of the internal and external valves 130, 120.

Ring ledge

The extreme end towards the inside of the housing 100 contains a connecting element for connecting directly or through some means of connection with the container. In the illustrated embodiment, the connecting element includes an annular protrusion 140, which must be connected to the container through a separate connector 300. The annular protrusion 140 extends from the outermost portion inwardly to the inner compartment 116 of the housing 100 and back to the outer end of the housing 100. The annular protrusion 140 in the illustrated embodiment the implementation is usually conical, extending outward from the extreme end inward.

The outer surface of the annular protrusion 140 may advantageously comprise recesses 142. In the described embodiment, the recesses 142 form a ladder shape on a conical annular protrusion 140.

CONNECTOR

4a-4c show an embodiment of a connector for connecting a pump of an embodiment to a container. Fig. 4a is a perspective view of a connector, Fig. 4b is a sectional view of a connector, and Fig. 4c is a top view of a connector.

The connector 300 typically comprises an annular base 308 including an opening in which the pump will be located. The inner flange 302 extends from the inner periphery of the base 308, and the outer flange 304 extends from the outer periphery of the base 308. The outer flange 304 includes two peripherally extending recesses 306 on the side facing the inner flange 302.

A recess 306 closest to the base 308 is provided for snapping into the furthest portion of the annular projection 140 of the housing for connecting the pump to the connector 300. Another recess 306 is snapped to engage the portion of the container 400, as will be described later.

It is generally believed that this is advantageous to having a connector 300 comprising snap-fit devices to provide snap-fit connections to the pump and tank. In addition, it is believed that other embodiments of connectors comprising such snap-in devices are possible compared to the one described. In particular, the shape, size and location of the snap-in devices may vary depending on the design of the housing connecting devices and the container.

PUMP ASSEMBLY AND RING

Advantageously, the pump is made, as in the illustrated embodiment, of only two parts. Preferably, one part includes a regulator 200 and the other includes a housing 100. Therefore, the pump can be easily assembled by inserting the regulator 200 into the housing 100 so that the locking element 200 of the regulator can be latched into the locking device in the housing 100. Therefore, the assembly of the pump is particularly easy and reliable. In the illustrated embodiment, the locking element consists of a locking plate 250, which is inserted with a snap into the locking device, which is the locking groove 117.

It is understood that the two parts are preferably made of resilient plastic. Thus, the elastic properties of the materials are also effective in performing snap-in insertion of the controller 200 in the housing 100. However, to ensure reliable interlocking, it is understood that the snap-in installation should be relatively stable. The necessary stability can be easily achieved by adjusting the structure and thickness of the material, for example, the thickness of the retainer plate 250 in the illustrated embodiment.

Furthermore, when used with the connector 300, as described above, the assembled pump is easily connected to the connector by inserting the housing through the annular opening of the connector 300 and providing a snap lock between the housing 100 and the connector 300. Consequently, a first snap-on installation of the controller 200 is provided. and cases 100 and a second snap-fit installation of the case and connector 300.

In the illustrated embodiment, the second snap-fit installation is provided by the extreme recess 142 of the annular protrusion 140 of the body 100, forming a snap-fit lock when inserted into the extreme recess 306 inwardly on the outer flange 304 of the connector 300. Consequently, the annular protrusion 140 fits between the inner flange 302 and an outer flange 304 of the connector.

Fig. 5a shows how the connector 300, the housing 100 and the regulator 200 can be inserted one into the other to form the connector-pump assembly.

Fig. 5b is a sectional view of the connector-pump assembly and shows how specific elements, as described above, are assembled together in the illustrated embodiment.

The outer valve 220 is located in the outer compartment 112 of the housing 100 with its edge 222 in contact with the wall of the chamber. 5b, the rod 210 is returned to its original state when the pump is empty or when it is used to pump relatively low viscosity fluids. It will be appreciated that if the rod 210 is elongated when pumping relatively high viscosity fluids, the bulge 224 of the outer valve 220 may be in contact with the flow control means 138 surrounding the dispensing opening 120.

The spacer 240 is located adjacent to the step 118 of the chamber wall, and it will be appreciated that when the shaft 210 is bent to tilt the outer valve 220, the spacer 240 will limit the bending movement by contacting the step 118 and / or other portions of the inner wall of the housing 100.

The middle compartment 114 of the housing 100 extends along the selected length and surrounds the rod 210. It is understood that the middle compartment 114 helps to evacuate the volume and provides space for bending of the rod 210. In addition, the middle compartment 114 is essentially a part of the chamber that will be compressed during evacuation , and therefore the size of the middle compartment is also important to ensure the suction power of the pump. As mentioned above, the wall thickness of the middle compartment can be selected to provide elasticity suitable for the pumping function.

However, in the inner portion of the middle compartment 114, the wall thickness is already increased to stiffen the pump structure before reaching the inner valve 130 (it can be noted that the wall thickness of the casing is relatively large that surround the inner valve 130 and the outer valve 120, but relatively small to form a pumping section between them). A section with relatively thick walls of the middle compartment 114 surrounds a guide member 260 located on the shaft 210, which is also a device for limiting the movements of the internal valve 130.

The internal valve 130 is visible in place with its edge 232 in contact with the ledge 119 of the housing 100. The stiffening element 234, which performs the function of controlling the internal valve 130, is surrounded by an internal compartment 116 of the housing.

Finally, the locking element 250 is in place in the locking groove 117 of the housing 100, securing the regulator 200 in the housing 100.

It will be appreciated that the illustrated embodiment of a pump comprising a housing 100 and a regulator 200 can be used with other connectors compared to the embodiment described herein. To this end, the housing 100 may naturally comprise a different connecting means 140 compared to the connecting means described herein.

However, it is believed that the illustrated connector is particularly advantageous due to its easy assembly and reliable connection, impervious to liquid. In this embodiment, the annular protrusion 140 is snapped into the connector 300 as described above. When the annular protrusion 140 is in place in the connector 300, it is seen that a space is formed between the annular protrusion 140 and the extreme protrusion 306 towards the inside of the connector 300. It is understood that a predetermined capacity can be accommodated in this space, and the extreme protrusion is used to lock with snap-fit. 306 toward the inside of the connector 300. Consequently, the recesses 142 on the annular protrusion 140 will function to increase friction and snap stability.

SYSTEM

6a-6c depict an embodiment of a metering system comprising a compressible container, pump, and connector, as described above. Fig. 6a is a perspective view of the metering system, Fig. 6b is a sectional view of the metering system, and Fig. 6c is a bottom view of the metering system.

The compressible container 400 is a predominantly semi-rigid type comprising a relatively rigid portion 410 and a compressible portion 420. Typically, a difference in stiffness of the portions can be obtained by forming sections with walls having different material thicknesses, the rigid portion 410 having a larger wall thickness than the compressible portion 420.

It is believed that the depicted container 400 is particularly advantageous, which contains only one hard portion 410 and one compressible portion 420. The compressible portion 420 may be compressed onto the rigid portion while emptying the bottle. During compression, the rigid portion 410 will provide sufficient support to maintain an adjustable position of the container 400 in, for example, a metering device. This is particularly advantageous when information is to be printed on the container, and it is desirable that said information is visible through, for example, a window in the metering device during the discharge process.

The depicted container 400 is longitudinally divided so that the rigid portion 410 approximately forms one longitudinal half of the container 400, and the contracting section 420 approximately forms the other longitudinal half. The outlet 430 is formed by extending from the end wall of the rigid portion 410. The outlet 430 forming part of the rigid portion 410 is advantageous from a manufacturing point of view and ensures that the position and configuration of the outlet 430 are stable.

On figs you can see how the pump 1 is located in the outlet 430 on the hard section 410 of the tank. In addition, it is seen that the rigid portion 410 in this case forms a substantially regular cylindrical longitudinal outer wall, while the compressible portion forms a slightly expanded configuration having a more complex shape, forming two convexities or gentle angles.

6b, the connection between the compressible tank 400 and the pump 1 by means of the connector 300 is shown with specific reference to enlarged part A. The connection between the pump 1 and the connector 300 has been described above. The container 400 includes a connecting element 432 at its outlet 430. The connecting element 432 is adapted to fit into the open space formed between the annular projection 140 of the pump and the outer flange 304 of the connector 300. To perform a snap lock between the connector 300 and the container 400, the connecting element 432 contains a rib 434 for interlocking with the extreme recess 306 in the direction inward of the connector 300. The strength of the internal connection of the parts is increased due to the recesses 142 of the annular protrusion 140, which Some will contact the inside of the connecting element 432 of the container 400 and increase friction, which counteracts the disassembly of the parts.

It is understood that, by snapping in all the elements, assembling the entire system is particularly easy. However, the connection is fluid tight and reliable, ensuring that neither air nor contaminants penetrate the system and that the system does not allow fluid to pass through.

Manufacture and materials

Advantageously, the regulator and the housing can advantageously be made of propylene-based materials. Materials must be selected to provide sufficient elasticity for the given functions. For functions that depend on the ability of the material to return to its original shape after curvature, it is believed that the parts should be able to return to their shape after at least 1000 curvatures in order to ensure function until the container is empty. This amount, of course, depends on the size of the container, and should only be considered as an approximate amount. Pumps were made in which the parts withstand at least 10,000 curvatures, which are significantly higher than the nominal requirements.

Advantageously, the regulator and the housing may be made of low density materials.

In addition, the pump materials must be selected so that they can be resistant to the pumped liquid, that is, therefore, without dissolution.

Preferably, the material or materials of the pump should be of the same type so that the pump can be disposed of as a single device without prior disassembly.

Advantageously, the regulator and the housing can be obtained by injection molding.

Advantageously, the container may be made of a material based on polypropylene or high density polyethylene. It is especially advantageous if the container is made of material of the same type as the pump materials, so that the entire metering system can be removed and disposed of as a single device.

Advantageously, the container may be blow molded.

It is easy to understand that many alternative embodiments are possible, including one or more of the aforementioned advantageous elements.

Claims (12)

1. A disposable pump (1) for a dispensing system for liquids, in particular for a dispensing system that contains a compressible container (400), the pump (1) comprising a chamber (110) in which the pressure can be changed to pump liquid from the container (400) to the chamber (110) and then from the chamber (110) to the metering hole (120), the housing (100) surrounding the internal valve (230) for regulating the fluid flow between the container (400) and the chamber (110), and the outer a valve (220) for regulating the flow of fluid between the chamber (110) and the metering hole (120), while pump (1) can take
- a closed position in which the volume of liquid is supplied from the container (400) to the chamber (110) under the influence of the negative pressure created in the chamber (110),
and a dispensing position in which a volume of liquid is supplied from the chamber (110) to the dispensing hole (120),
characterized in that it contains
an internal valve (230), which is a one-way valve for opening the fluid flow in the metering direction at the opening pressure of the internal valve acting in the metering direction and closing at any pressure acting in the opposite direction of the metering
an external valve (220), which is a two-way valve, for opening the fluid flow in the dispensing direction or in the direction opposite to the dispensing direction with the opening pressure of the external valve, depending on the direction of the opening pressure of the external valve,
moreover, said internal valve (230) and said external valve (220) are located on a regulator (200), which is fixedly located in the housing (100), said housing (100) including a chamber (110) and a metering hole (120),
so that when the pump (1) moves from the dispensing position to the closed position and a negative pressure is created in the chamber (110),
the pressure difference between the container (400) and the chamber (110) causes the opening of the internal valve (230) to allow the passage of fluid from the container (400) into the chamber (110), and
the pressure difference between the metering hole (120) and the chamber (110) causes the external valve (220) to open to allow the liquid to be sucked back from the metering hole (120) to the chamber (110). 2. The pump according to claim 1, in which
when the pump (1) is in its dispensing position, the outer valve (220) forms said two-way valve, and
when the pump (1) is in its closed position, the outer valve (220) creates a seal between the chamber (110) and the metering hole (120),
so that when the pump (1) moves from the dispensing position to the closed position, the outer valve (220) will first open to allow liquid or air to be sucked back from the metering hole (120) into the chamber (110), and then, when the closed position is reached , create a seal between the chamber (110) and the metering hole (120). 3. The pump according to claim 1 or 2, in which, when the pump (1) is in its dosing position, the external valve (220) takes an inclined position in the chamber (110), and when the pump (1) is in its closed position, the outer valve (220) takes a symmetrical position in the chamber. 4. The pump according to claim 1, in which the opening pressure of the internal valve (230) is less than the opening pressure of the external valve (220), so that the external valve (220) will close before the internal valve (230), since the negative pressure in the chamber is equalized. 5. The pump according to claim 1, in which the internal valve (230) when in the closed position has a contact area with the chamber (110), which is larger than the contact area of the external valve (220) when in the closed position. 6. The pump according to claim 1, in which the outer valve (220) when it is in the closed position in the chamber (110) is compressed at the periphery relative to the uncompressed state of the outer valve (220), and the difference between the diameter of the chamber (110) at a location located in contact with the external valve (220) when located in the closed position, and the diameter of the external valve (220) when in an uncompressed state, is 0.09-0.20 mm, preferably 0.10-0.20 mm, most preferably 0, 10-0.15 mm. 7. The pump according to claim 1, in which the inner valve (230) when in the closed position in the chamber is compressed at the periphery relative to the uncompressed state of the inner valve (230), and the difference between the diameter of the chamber (110) at the location at which the inner valve ( 230) is compressed around the periphery, and the diameter of the internal valve (230) when in said uncompressed state is 0.20-0.35 mm in the circumferential direction, preferably 0.25-0.35 mm, most preferably 0.25-0 , 30 mm. 8. The pump according to claim 1, in which the internal valve (230) is essentially parabolic. 9. The pump according to claim 1, in which the internal valve (230) comprises an edge (232) that is able to move out of tight contact with the chamber (110), said edge (232) forming an angle α with the longitudinal axis of the pump 1, in which the angle α is in the range of 15-30 °, more preferably 20-30 °, most preferably 20-25 °. 10. The pump according to claim 1, in which the external valve (220) has an external shape, at least partially repeating the contour of the ball. 11. The pump according to claim 9, in which the outer shape of the outer valve (220) follows the contour of the ball to form at least half of the ball. 12. The pump according to claim 1, in which the outer valve (220) contains an edge (222), which is able to move in tight contact with the chamber (110) and from it, and said edge (222) when the pump is in its closed position is held between the parallel walls of the chamber (110) and runs parallel to the walls.

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