CN118019594A - Spring made of plastic and output device - Google Patents

Abstract

A spring made of plastic, an output device provided with the spring for a particularly cosmetic product and the use of the spring are provided, wherein the spring is made of a material mixture with propylene and has a particular characteristic value for achieving good spring characteristics.

Description

Spring made of plastic and output device

Technical Field

The invention relates to a spring made of plastic according to the preamble of claim 1 or 2, an output device according to the preamble of claim 17 and the use of a spring according to the preamble of claim 19.

The term "output device" is understood in the present invention to mean preferably a device for outputting a product, preferably a liquid, particularly preferably as an aerosol, in particular in a spray manner, which output device is preferably manually operable.

The pump or the output device preferably has at least one functional spring in the sense of the invention, which is associated with a pump piston and/or a valve, for example. Metal springs have been mainly used so far. Plastic springs, which are increasingly being preset as alternatives to metal springs, often do not have good or satisfactory spring characteristics.

Background

Document WO 2004/065095 A1 discloses a spiral compression spring made of plastic, which is formed as an injection molded part, wherein the spiral section adjoining the joint surface has a specific pitch on at least one sideSmaller slope. By means of the non-uniform inclination of the thread pitch, the spring characteristic curve is non-linear, so that the spring does not show an optimal spring characteristic. The plastics are not described in further detail.

Document EP 1,506,818 B2 discloses a pressure accumulating liquid ejector having two elastic elements, wherein a first elastic element resets the pump piston and a second elastic element forms the element of the outlet valve. Polyethylene, polypropylene, nylon, acrylonitrile-butadiene-styrene, polyethylene terephthalate, polybutylene terephthalate, polyoxymethylene can be used as the material of the elastic elements and components of the accumulator type liquid ejector manufactured in an injection molding manner.

Document WO 2009/094793 A1 discloses a plastic spring which can be used mainly in devices for applying cosmetics. The plastic spring is preferably injection molded from a thermoplastic. The spring may be made of only plastic, which is not described in further detail, but alternatively, for example, reinforcing fibers or other elements may also be embedded in the plastic. The plastics are not described in further detail.

Document DE 44 41 A1 discloses a discharge device which comprises a working section with a spring section which can be designed as a spiral or torsion spring with a closed spring sleeve. The discharge device or the corresponding working segment is produced as an injection molded part made of plastic, which may be a copolymer, such as polyethylene, polypropylene or other thermoplastic.

Document FR 2 969 241 discloses a plastic spring, which consists of a ring and an elastic element. In the case of compression, torsion forces occur in each spring plane, which are macroscopically balanced with respect to one another, so that the spring can be compressed overall without torsion forces. The ring of the spring is made of hard plastic and the resilient element of the spring is made of soft plastic. The plastics are not described in further detail.

Document US2003/0209567 A1 discloses a structure for spraying products. The structure has exactly one spring made of plastic. Various embodiments of the spring are described. The spring is preferably made of polyoxymethylene, polyethylene or polypropylene.

Document EP 1,375,011 B1 discloses a metering device comprising a bellows spring made of plastic, wherein the bellows spring is formed in one piece with an outlet valve. The plastics are not described in further detail.

Document US10,543,500B2 discloses a fluid pump with a spring, wherein styrene block copolymers, polyolefins, elastomeric alloys, thermoplastic polyurethanes, thermoplastic copolyesters and thermoplastic polyamides are suitable materials for the spring. In the case of polyolefins, it is possible to use mixtures composed of at least two different polyolefins and/or copolymers composed of at least two different monomers. In one embodiment, a thermoplastic from a group of thermoplastic polyolefin mixtures, for example from a group of polyolefin copolymers, is used. Also suitable are groups of ethylene alpha olefin copolymers. Among them, ethylene-1-octene copolymers have proven particularly suitable.

Document DE 44 11 031 A1 discloses a handle-operated pump for delivering a liquid or pasty medium. The return spring of the pump handle is designed as a bellows spring, which is produced by injection molding and consists of plastic, for example polypropylene or polyethylene.

Document DE 694 26t2 discloses a pump device with a collapsible pump chamber. The pump chamber is a bellows having an elastic modulus of less than 10.000 psi. Disclosed as exemplary materials are polyolefins such as low density polypropylene, polyethylene, very low density polyethylene, and ethylene vinyl acetate.

Document DE 43 90 813 T1 discloses a hand-held sprayer comprising a body and a pump mechanism having a trigger (Abzug) which is movably supported on the body. A plastic spring structure is placed between the body and the trigger to always press the trigger back to the original position. The spring structure comprises two leaf springs which are interconnected at their ends by ribs. The leaf springs are manufactured from a glass-fibre-reinforced plastic material, such as for example a mixture of polypropylene and polyurethane (nylon) +30 wt.% glass fibres.

Document WO 2020/156 935a1 discloses a dispenser for dispensing flowable, for example liquid or pasty materials. The output device has a restoring device in the form of a plastic spring, comprising a lower spring ring and an upper spring ring, which are connected to one another in a compressible manner by means of a spring damper. As plastic for the spring, polypropylene with filler can be used.

Document US10,543,500B2 discloses a fluid pump comprising a thermoplastic spring. The spring has a plurality of diamond spring sections.

The known plastic springs are not optimal for the output device, which should be easy to operate manually and have a high service life.

Disclosure of Invention

The object of the invention is to provide a spring made of plastic, in particular for an output device, an output device having a spring made of plastic, and the use of a spring made of plastic, wherein the spring has a force-displacement diagram that is as linear as possible, is easy to handle and/or is as resistant to fatigue and/or hysteresis-free as possible, enables simple or complete recovery and/or is simple in construction and is cost-effective.

The above object is solved by a spring according to claim 1 or 2, an output device according to claim 17 or a use according to claim 19. Advantageous developments are the subject matter of the dependent claims.

The first aspect of the invention is that the spring is preferably capable of being reversibly compressed by at least 10% and/or the elastic modulus of the plastic is less than 1500MPa. Experiments have concluded that: such springs exhibit good spring characteristics and in particular can be operated easily and comfortably, in particular when the springs are compressed by a maximum of 20 or 30% starting from a relaxed state.

In addition, tests have surprisingly shown that a decrease in the modulus of elasticity of the spring material of the spring is accompanied by a greater reversible compression.

A second, yet independently implementable aspect of the invention is that the spring is preferably constructed such that the characteristic value K1 is less than 0.05[ n/mm2.5] until at least 10% compression is achieved, where k1= (w·l0.5)/(v·s2), where W is the work done to compress the spring from a relaxed state by displacement S and V is the plastic volume of the elastic section. Experiments have shown that: the plastic springs thus constructed exhibit good spring properties and in particular have very good fatigue resistance.

A third, likewise independently implementable aspect of the invention is that the spring is constructed such that at least 10% compression is achieved, the characteristic value K2 is less than 0.005[ mm-3.5], where k2= (w·l0.5·ra)/(v·af·e·s2), where W is the work done to compress the spring from the relaxed state by displacement S, RA is the outer diameter of the elastic section, AF is the filling coefficient of the relaxed elastic section (Ausf u llfaktor), E is the elastic modulus of the material of the elastic section, and V is the plastic volume of the elastic section. Experiments have confirmed that: the plastic spring thus constructed exhibits good spring properties and is particularly at least as hysteresis-free as possible.

A fourth, likewise independently implementable aspect of the invention is that the plastic of the spring or elastic section is preferably a material mixture comprising polypropylene as a base component and at least one additional component, wherein the material mixture is formed from the base component by at least 50% by weight and at most 95% by weight.

The basic component alone is not suitable as spring material, since the spring cannot be compressed sufficiently reversibly, in particular only to about 5%. The reason for this is the structure of the basic component, which is described from the image as consisting of filaments linked in all three dimensions. By adding additional components, the filaments are linked only in two dimensions, i.e. in planes, whereby the planes can be reversibly moved relative to each other in a limited range. From the point when the ratio of the additional components reaches a certain threshold, the spring can be compressed very strongly without breaking there, but then without returning to its original shape, because the material flows, i.e. is too easily plastically deformed. The optimum material mixture, in particular for the preferred spring shape, was determined experimentally.

The fifth, yet independent aspect of the invention is that the plastic is a material mixture comprising polypropylene as a base component and at least one additional component, wherein the plastic has a density of 0.9g/cm3 or less and/or the additional component has a density of less than the base component. Very good elastic properties can thus be achieved, as already demonstrated by the test.

Preferably, the additional component has polyethylene, ethylene-octene copolymer, and/or isotactic propylene repeating units with random ethylene distribution. These materials are particularly suitable as additional components, since they can be mixed excellently with the basic components and bring about good elastic properties, as has been demonstrated in tests.

Preferably, the additional component has an elastic modulus of less than 1000MPa; and/or the modulus of elasticity of the base component is greater than 1000MPa. The modulus of elasticity of the material mixture can thus be set very well by the ratio of the components to one another, wherein tests have shown that the modulus of elasticity of the material mixture has a nonlinear relationship with the ratio of the additional components.

Preferably, the spring according to the invention is manufactured by injection moulding. In this way, the spring can be produced very cost-effectively and in a very large number of pieces.

Preferably, the spring shape is designed such that the spring shape does not form a undercut on the injection tool side during its production. Preferably, the spring can thereby be removed from the injection molding tool in a simple manner, in particular without damage.

The spring according to the invention preferably forms the valve member of the inlet valve and/or the outlet valve. This facilitates a compact and simple construction, in particular of the pump or output device.

A sixth, yet independent aspect of the invention relates to an output device, in particular a manually operable output device, having at least one spring according to the invention, in particular made of plastic according to one of the above aspects, for example for resetting a pump piston and/or an inlet valve or an outlet valve. In particular, this makes it possible to provide the output device with very good user-friendliness or easy operability and/or complete recyclability over a long service life.

A seventh, yet independent aspect of the invention relates to an output device, in particular a manually operable output device, having at least one spring made of plastic, for example for resetting a pump piston, wherein the difference between the resetting force of the spring in the maximally compressed state and the resetting force of the spring in the minimally compressed state is less than 20N, preferably less than 15N, particularly preferably less than 10N. This may allow the force required to operate the output device to be increased only slightly during operation. This is advantageous for high user friendliness.

An eighth, yet independent aspect of the invention relates to an output device, in particular a manually operable output device, having at least one spring made of plastic, for example for resetting a pump piston and/or as a valve element of an inlet valve or outlet valve, wherein the spring is preloaded or compressed in the output device by at least 5%, in particular 10%, in a minimum compressed state and the spring is compressed in the output device by less than 30%, in particular less than 25%, particularly preferably less than 20%, in a maximum compressed state. Experiments have shown that the springs exhibit a high stability just in this range.

In particular, plastic deformation of the spring is avoided by a preset limit to the maximum compression of the spring in the final state. In this way, the service life or service time of the output device can be increased by the minimum and maximum compression of the spring.

Preferably, the spring is preloaded or minimally compressed in the initial state of the output device and/or maximally compressed in the final state of the output device. This makes it possible to make the structure of the output device simple and compact.

A ninth, yet further, independently implementable aspect of the present invention relates to a spring according to the present invention as a return element for a pump piston and/or an inlet valve or an outlet valve of a particularly preferably manually operable output device for outputting a fluid or a product, preferably a cosmetic product. This gives corresponding advantages.

The plastic spring according to the invention solves or reduces in particular the problems of undesired rapid fatigue, undesired or strong hysteresis and/or undesired or strong deviations from the linear spring characteristic curve of other plastic springs.

Furthermore, the spring according to the invention makes it possible to provide the output device or pump according to the invention with a simple structure, temperature, compactness and/or cost-effectiveness; and/or support the clean delivery or delivery of the product to/from the delivery device or pump according to the invention, and/or support the delivery device or pump with complete or simple recyclability.

The above-described aspects and features of the invention, which result from the claims and the following description, can in principle be realized independently of one another, but also in any combination.

Drawings

Further aspects, advantages, features and characteristics of the present invention result from the claims and the following description of preferred embodiments according to the accompanying drawings. In the drawings:

Fig. 1 shows a schematic section through a pump or output device according to the application, comprising a spring according to the application as a main spring and a spring according to the application as an outlet spring;

Fig. 2 shows a schematic view of a main spring according to a first embodiment;

fig. 3 shows a schematic longitudinal section of the spring according to fig. 2;

fig. 4 shows a schematic view of a main spring according to the application according to a second embodiment;

fig. 5 shows a schematic longitudinal section of the spring according to fig. 4;

Fig. 6 shows a schematic view of a main spring according to the application according to a third embodiment;

FIG. 7 shows a schematic front view of the spring according to FIG. 6;

fig. 8 shows a schematic longitudinal section of the spring according to fig. 6;

fig. 9 shows an enlarged view of the dot-dash line area of fig. 6;

fig. 10 shows a schematic view of a main spring according to the application according to a fourth embodiment;

FIG. 11 shows a schematic front view of the spring according to FIG. 10;

fig. 12 shows an enlarged view of the dotted area of fig. 10;

fig. 13 shows a schematic view of a main spring according to the application according to a fifth embodiment;

fig. 14 shows a schematic longitudinal section of the spring according to fig. 13;

Fig. 15 shows an enlarged view of the dot-dash line area of fig. 13;

fig. 16 shows a schematic view of a main spring according to the application according to a sixth embodiment;

fig. 17 shows a schematic longitudinal section of the spring according to fig. 16;

fig. 18 shows a schematic view of an outlet spring according to the application according to a first embodiment;

FIG. 19 shows a schematic front view of the spring according to FIG. 18;

FIG. 20 shows a schematic longitudinal section of the spring according to FIG. 18;

FIG. 21 shows a first graph;

FIG. 22 shows a second graph;

fig. 23 shows a schematic view of an outlet spring according to the application according to a second embodiment; and

Fig. 24 shows a schematic cross section of an outlet spring according to the application according to a second embodiment.

In the drawings, which are not to scale and are merely schematic, the same reference numerals are applied to the same, identical or similar components and assemblies, wherein corresponding or similar features and advantages are achieved even if repeated descriptions are omitted.

Detailed Description

Fig. 1 shows a schematic longitudinal section of an output device 1 or a pump 7 according to the application, comprising one or two springs 9, 16 according to the application.

The output device 1 or pump 7 is preferably used for outputting a product 2, preferably a fluid or a liquid, in particular as a spray, mist and/or aerosol.

Particularly preferably, the fluid or product 2 is used for cosmetic purposes or for cosmetic care. For example, hair spray, styling foam, sunscreens, or the like.

However, the output device 1 or the pump 7 can also be used for cleaning products, household products or other products 2.

Preferably, the output device 1 has a container 3 for the product 2, an output head 4, a connection piece 5, a housing piece 6 and/or a pump 7.

The output device 1 or the pump 7 is preferably designed such that the product 2, in particular a predetermined quantity of the product 2, is sucked or conveyed out of the container 3, under pressure and/or is output under pressure.

It is preferably possible to make the fluid or the product 2 output through the output head 4 or the nozzle 4A of the output device 1.

The output device 1 or the pump 7 is preferably mounted on the container 3 or connected thereto, for example locked or screwed, by means of the connecting piece 5 and/or the housing piece 6. In the embodiment shown, the outlet head 4 or the housing part 6 is preferably connected or connectable to the container 3 by means of a connecting element 5, preferably in form-locking, force-locking and/or material-locking, in particular by screwing. However, solutions are also possible in which the outlet head 4 or the housing part 6 has or forms a connection 5 and/or the outlet head 4 is connected or connectable to the container 3 in a non-spatial or direct manner.

In particular, the connection piece 5 and/or the housing part 6 hold the pump 7 or its pump housing 8 on the outlet side.

In this example, the housing part 6 is fixedly connected or locked to the pump housing 8 or forms part of the pump housing 8.

The pump 7 is preferably at least partially or completely arranged within the container 3.

Preferably, the output device 1 or the pump 7 has a pump housing 8, a spring 9 according to the application in the form of a main spring, a pump piston 10, an inlet valve 11, an outlet valve 14 and/or a (further) spring 16 according to the application in the form of a valve spring or an outlet spring.

The output device 1 or the pump 7 preferably has a rising line 17, which is connected in particular to the end or the inlet of the pump 7, preferably in order to be able to receive the product 2 or to suck it out of the container 3.

The inlet valve 11 preferably has an inlet valve body 12 and an inlet valve seat 13.

Preferably, the outlet valve 14 has an outlet spring 16 and/or an outlet valve body 15 and an outlet valve seat 18, wherein the outlet valve spring 16 is formed in one piece with the outlet valve body 15 and/or presses or pretensions the outlet valve body against the outlet valve seat 18 into a closed position or closes the outlet valve 14.

In particular, the outlet valve 14 is provided on or in the pump piston 10.

Preferably, the pump piston 10, in particular a piston rod or hollow section 10A of the pump piston 10, protrudes axially from the pump housing 8 or the housing part 6 and/or axially to the outlet head 4. Particularly preferably, the housing part 6 or the pump housing 8 has an (axial) opening through which the piston 10 or the section 10A extends outwards or in the direction of the outlet head 4.

Preferably, the housing part 6 or the pump housing 8 has an axial stop 6A for the pump piston 10.

Preferably, the pump 7 or the outlet valve 14 or the pump piston 10 has an outlet, in particular wherein the outlet is in fluid connection with the outlet head 4.

The output head 4 is preferably fastened and/or fluidically connected to the piston 10, in particular by means of a rod or a section 10A.

Preferably, an outlet valve 14 or an outlet valve body 15 and/or an outlet spring 16 is provided in the pump piston 10 or the section 10A and/or in the outlet head 4 and/or between the pump piston 10 and the outlet head 4. In particular, the outlet spring 16 is supported at one end on the outlet head 4 and/or at its opposite end on the pump piston 10.

In particular, the outlet spring 16 is mounted pretensioned.

Preferably, the pump housing 8, the inlet valve 11 and the outlet valve 14 or the pump piston 10 form or delimit a pump chamber 7A of the pump 7.

Preferably, a main spring 9 is arranged in the pump chamber 7A or in the pump housing 8.

Preferably, the main spring 9 is supported at one end on the pump piston 10 and/or at its opposite end on the pump housing 8 or the inlet valve body 12.

In particular, the pump piston 10 is pressed or preloaded into the closed state or initial state by the main spring 9.

In particular, the main spring 9 is mounted pretensioned.

Preferably, the output device 1 or the pump 7, the pump housing 8 has a longitudinal axis a.

Preferably, the pump 7or the pump chamber 7A can flow through the pump or the pump chamber from the inlet to the outlet, either axially or along the longitudinal axis a and/or the fluid/product 2.

Preferably, the pump housing 8, the inlet valve 11, the outlet valve 14 and/or the pump piston 10, the main spring 9 and/or the outlet spring 16, particularly preferably all components or assemblies of the output device 1 or the pump 7 are produced from plastic and/or injection molded.

Preferably, the pump 7 is designed as a volumetric pump, in particular as a dosage pump or piston pump.

By operating the output device 1, or depressing the output head 4, or displacing the pump piston 10 downwards or in the direction of the container 3, the pressure in the pump chamber 7A (preferably with a predetermined amount of product 2 located therein) is preferably increased, the volume of the pump chamber 7A is reduced, the main spring 9 is compressed and/or the output device 1 is brought into a final state.

Particularly preferably, the outlet valve 14 opens (automatically) when a certain pressure is exceeded in the pump chamber 7A or the volume of the pump chamber 7A is reduced by means of the pump piston 10, in particular by compressing the outlet spring 16. In this way, in the event of a certain pressure being exceeded (opening pressure), the product 2 is caused to be output from the pump chamber 7A through the outlet to the output head 4 and optionally, in particular by means of the nozzle 4A, to be sprayed out or otherwise output.

After the output of the product 2, or after the pump operation or the pump movement has ended, or after the end state of depression has been reached, the pressure is reduced and the outlet valve 14 is closed again automatically.

After the end of the depression of the output head 4, the pump piston 10 or the output head 4 is returned or returned to the initial state, preferably by a restoring force or the release of the main spring 9. Preferably, the pressure in the pump chamber 7A is thereby further reduced or negative pressure is generated, so that the inlet valve 11 is opened and the product 2 is sucked from the container 3 through the inlet into the pump chamber 7A.

Preferably, the inlet valve 11 closes again automatically after the pressure equalization or in the next operation (depression of the piston 10) as a result of the pressure increase.

Preferably, the inlet valve body 12 of the inlet valve 11 is formed as a long rod and/or extends along the longitudinal axis a.

The inlet valve body 12 is preferably designed or dimensioned in such a way that it can open the outlet valve 14 or can lift the outlet valve body 15 from the outlet valve seat 18 before the pump piston 10 has reached its compressed end position for a short time. In particular, this is important in the case of first use in order to expel air from the pump chamber 7A in the case of so-called first use and to be able to fill the pump chamber 7A with fluid/product 2.

The initial state of the output device 1 or of the pump 7 shown in fig. 1 is preferably a state of the pump 7, in particular of the pump piston 10 or of the output head 4, which is occupied in the non-operating state and/or automatically or by the spring force of the main spring 9. In the initial state, the volume of the pump chamber 7A is maximum and/or the main spring 9 is released (yet preloaded) and/or the pump piston 10 or the output head 4 is in its upper end position or rest position.

The final state of the output device 1 or of the pump 7 is preferably the state of the pump 7, in particular of the pump piston 10 or of the output head 4, which is assumed when the volume of the pump chamber 7A is minimal and the outlet valve 14 is open.

In the final state (operating or depressed state), the pump piston 10 occupies its lower end position in the view according to fig. 1, and the output head 4 is in its depressed end position.

In the final state, the outlet valve 14 is preferably forced open by the inlet valve body 12.

The final state is preferably mechanically limited, for example by the outlet head 4 being stopped on the container 3, the connecting part 5 or the housing part 6 or by other means.

Alternatively or additionally, the inlet valve body 12 may also form an end stop for the pump piston 10.

In this example, the inlet valve body 12, the outlet valve body 15 or the outlet spring 16 preferably hits the outlet valve body 15 or the outlet spring 16 before reaching the final state for a short time, so that the outlet spring 16 acts as a buffer or brake with in particular an increasing force until the pump piston 10 and the outlet head 4 actually reach the end position or the final state.

Preferred aspects and features of the springs 9 and 16 according to the application are further elucidated below with reference to the further figures. Wherein the description of the main spring 9 applies correspondingly or additionally also to the outlet spring 16 and vice versa, and no further description is necessary.

Fig. 2 shows a first embodiment of the main spring 9 according to the application in a perspective view, which is also shown in the example according to fig. 1. Fig. 3 shows this main spring 9 in a longitudinal section.

Fig. 2 and 3 show the main spring 9 in a relaxed, i.e. relaxed or uninstalled state.

Preferably, the main spring 9 has a (central) spring axis B. In particular, the spring axis B extends along or coaxially to the longitudinal axis a of the output device 1 or the pump 7 when the main spring 9 is installed.

The main spring 9 has an elastic section 9F, which is preferably at least substantially or exclusively responsible for the elastic properties of the main spring 9.

Preferably, the main spring 9 has a first or here lower end section/seat 9C and/or an upper end section/seat 9D.

Preferably, the lower seat 9C and/or the upper seat 9D form an axial end of the main spring 9.

Preferably, the main spring 9 or the elastic section 9F has one or more preferably at least substantially circumferentially extending spirals or webs 9B and/or one or more preferably at least substantially axially extending holders 9A.

Preferably, the main spring 9 or the elastic section 9F forms at least substantially a hollow cylinder.

Particularly preferably, the web 9B and the carrier 9A form a hollow cylinder section 9F with a radially perforated main spring 9 or elastic section 9F.

The elastic section 9F has a plastic volume V which is smaller than the volume of a corresponding hollow cylinder without perforations, undercut and the like due to the perforations.

It should be noted that the main spring 9 or the elastic section 9F may also have a different shape than a hollow cylinder, for example by increasing and/or decreasing the inner diameter and/or the outer diameter. The plastic volume V of the elastic section 9F is accordingly determined by the volume of material actually used to form the elastic section 9F.

The plastic volume V is always determined in the uninstalled state of the main spring 9, i.e. in the relaxed state.

Preferably, the axial height H2 of the support 9A is the minimum axial spacing of two adjacent webs 9B in the region where the support 9A is connected to the webs 9B.

Preferably, the axial height H1 of the web 9B is defined by the axial spacing between the axially lowest point of the web 9B and the axially highest point of the web 9B.

Preferably, the axial thickness of the web 9B is defined by the axial spacing between the axially lowest point of this circumferential section of the web 9B and the axially highest point of this circumferential section of the web 9B over an infinitely small circumferential section of the web 9B.

Preferably, the axial thickness of the connecting piece 9B is constant or varies in the circumferential direction. In particular, the axial thickness of the web 9B is constant in the circumferential direction in the case of the main spring 9 of the first embodiment.

Preferably, the axial thickness of the stent 9A is defined by the axial spacing between the axially lowest point of the circumferential section of the stent 9A and the axially highest point of the circumferential section of the stent 9A on an infinitely small circumferential section of the stent 9A.

Preferably, the axial thickness of the holder 9A is constant or varies in the circumferential direction. In particular, the axial thickness of the carrier 9A is unchanged in the circumferential direction in the case of the main spring 9 of the first embodiment.

Preferably, the height H2 is greater than the height H1, in particular the ratio of the axial height H2 to the axial height H1 is greater than 1.2.

Preferably, the cross section of the connecting piece 9B is at least substantially rectangular.

Preferably, the cross section of the support 9A is at least substantially rectangular.

The cross section of the connecting piece 9B, the bracket 9A or the springs 9, 16 is preferably understood to be a section with a section plane perpendicular to the main extension plane of the connecting piece 9B, the bracket 9A or the springs 9, 16.

Preferably, the lower bearing 9C and/or the upper bearing 9D exhibit at least substantially no elastic action in the axial direction, or the bearing seats form hard and/or hollow cylindrical or annular bearing sections.

Preferably, the elastic section 9F is connected to the first and/or second support 9C, 9D with one or more axially oriented brackets 9A, in particular with two brackets 9A on opposite sides, i.e. offset by 180 °.

Preferably, one and/or several webs 9B, in particular in the first embodiment, the webs 9B, which are 360 ° encircling or annular, and the two holders 9A form a spring layer 9E.

Preferably, the elastic section 9F is formed from a plurality of repeated and in particular identical spring layers 9E, wherein an incomplete spring layer 9E can also be present or provided in the case of a transition to the support 9C or 9D, for example by omitting the webs 9B.

In the first embodiment, the web 9B, which surrounds, i.e. forms a closed loop, is also understood to be, or is formed as, a plurality of web portions or webs 9B, in which case two or four web portions or webs 9B extend from one carrier 9A up to the same spring layer 9E or the next carrier 9A of two spring layers 9E.

Preferably, the axial height or thickness of the spring layer 9E is produced by the sum of the height H1 and the height H2.

Preferably, the axial height of the spring layer 9E of the relaxed main spring 9 is greater than 1mm, preferably greater than 2mm, and/or less than 12mm, preferably less than 9mm.

Preferably, the holders 9A of the spring layer 9E are arranged rotationally symmetrically with respect to the spring axis B, preferably wherein the rotationally symmetrical countability corresponds to the number of holders 9A and is 2 in the case of the first embodiment.

Preferably, each complete spring layer 9E has a complete connecting piece 9B consisting of a plurality of connecting piece portions and one or more brackets 9A.

The web 9B is in particular complete when it extends 360 ° around the spring axis B and optionally after one complete rotation around the spring axis B and to itself.

Preferably, the holders 9A of the spring layer 9E are evenly distributed in the circumferential direction around the spring axis B.

Preferably, the holders 9A of the spring layer 9E are identically constructed.

Preferably, a connecting piece 9B is provided below and/or above (respectively) the support 9A.

Preferably, the region of the connecting piece 9B extending from one bracket 9A to the nearest bracket 9A is referred to as a connecting piece portion.

Preferably, the number of connecting piece portions of the connecting piece 9B of the spring layer 9E is the same as the number of brackets 9A of the spring layer 9E.

Preferably, the support 9A of the relaxed main spring 9 extends parallel to the spring axis B or in the axial direction. Alternatively, the bracket 9A may be inclined in the circumferential direction. In particular, the support 9A can be inclined toward the spring axis B or away from the same. Additionally, the support 9A can be bent so that the axial inclination of the support 9A can be varied in circumferential direction, in particular a plurality of times. Further the support 9A may be curved.

Bending preferably means: the cross section varies in the axial and/or circumferential direction, in particular a plurality of times.

In particular, the carrier 9A of the relaxed main spring 9 of the first embodiment extends parallel to the spring axis B or in the axial direction.

Preferably, the web 9B of the relaxed main spring 9 extends parallel to a radial plane of the main spring 9, which is in particular perpendicular to the spring axis B. Alternatively, the web 9B may be inclined in the circumferential direction, in particular in such a way that the main extension plane of the web 9B is inclined with respect to the radial plane of the main spring 9. Additionally, the web 9B can be bent so that the axial inclination of the web 9B can be varied in the circumferential direction, in particular a plurality of times. Furthermore, the connecting piece 9B may be curved.

In particular, the web 9B of the relaxed main spring 9 of the first embodiment extends parallel to a radial plane of the main spring 9, which is in particular perpendicular to the spring axis B.

Preferably, the support 9A occupies a width in the circumferential direction around the spring axis B and/or a radial width perpendicular to this width and perpendicular to the axial thickness. Preferably, the width and/or radial width of the support 9A varies axially. Preferably, the support 9A has a minimum width and/or a radial width and/or a maximum width and/or a radial width.

In particular, the width and/or radial width of the support 9A of the relaxed main spring 9 of the first embodiment is unchanged in the axial direction.

Preferably, the width and/or radial width of the support 9A is greater than 0.5mm, preferably greater than 1mm, and/or less than 8mm, preferably less than 5mm.

The number of brackets 9A of the spring layer 9E is not limited to two. For example, a spring layer 9E may also have only one support 9A and/or three supports 9A and/or four supports 9A and/or five supports 9A and/or any number of supports 9A.

The number of spring layers 9E of the main spring 9 is preferably greater than 3, preferably greater than 5, and/or less than 20, preferably less than 15.

Preferably, the holders 9A of the or each spring layer 9E are arranged equidistantly around the spring axis B or the holders 9A of the spring layer 9E are spaced differently radially around the spring axis B.

Preferably, all spring layers 9E have the same number of brackets 9A.

Preferably, the holders 9A of two adjacently arranged spring layers 9E are arranged rotationally or offset relative to one another about the spring axis B, preferably rotationally or offset relative to one another by 45 °, in particular by 60 °, particularly preferably by 90 °. Preferably, the offset angle is 180 ° times the number of brackets 9A of the spring layer 9E.

Preferably, the period of the stacking sequence of the spring layers 9E is 2. Thus, for example, the first, third and fifth spring layers 9E are identical to each other with respect to their rotational position and/or the second, fourth and sixth spring layers 9E are identical to each other with respect to their rotational position.

Alternatively, the stacking sequence of spring layers 9E may also have a larger period, preferably wherein a plurality of identical axially mutually rotated spring layers 9E are arranged adjacent to each other, and/or different spring layers 9E are arranged adjacent to each other, and/or a combination of the above variants is achieved.

The period of the stack sequence of spring layers 9E generally indicates in the present invention the number of adjacently arranged spring layers 9E until the stack sequence has taken over itself, e.g. the period of the stack sequence ABABAB is 2 and the period of the stack sequence ABCCABABCCAB is 6, wherein the letters indicate the spring layers 9E.

Preferably, the total number of connection pieces 9B of the spring 9 is an odd number.

Preferably, the bracket 9A provided on the lower support 9C is axially rotated with respect to the bracket 9A provided on the upper support 9D.

Preferably, the main spring 9 or the elastic section 9F is hollow or at least essentially hollow cylindrical.

Preferably, the ratio of the outer diameter RA of the elastic section 9F to the inner diameter RI of the elastic section 9F is greater than 1.05, preferably wherein the proportional outer diameter RA and inner diameter RI are located at the axial height of the elastic section 9F.

Preferably, the ratio of the length L of the elastic section 9F to the outer diameter RA of the elastic section 9F is greater than 1.2.

Preferably, the main spring 9 can be compressed along its spring axis B.

Preferably, the support 9A remains at least substantially parallel to the spring axis B in case the spring 9 is compressed.

Preferably, the connecting piece 9B is deformed with the main spring 9 compressed.

Preferably, the expansion of the web 9B, which is deformed by the compression of the main spring 9, is at least substantially sinusoidal or wave-shaped, wherein the midline of the web 9B is observed.

In the following, further embodiments of the main spring 9 are illustrated in accordance with further figures, wherein the previous embodiments and illustrations are applicable in particular correspondingly or complementarily even if not described in more detail, and only differences with respect to the first embodiment are mainly described.

Fig. 4 shows a second embodiment of the main spring 9 according to the application in a schematic view. Fig. 5 shows a schematic longitudinal section of the main spring 9 according to fig. 4.

The second embodiment of the main spring 9 differs in particular from the first embodiment in that each spring layer 9E of the main spring has exactly one support 9A.

The holders 9A of two adjacent spring layers 9E are preferably arranged radially rotated 180 ° relative to each other.

Preferably, the spring shaft B is zigzag-bent in the case of compression of the main spring 9. Preferably, the microscopic curvatures of the spring axes B are macroscopically balanced with each other.

Preferably, the support 9A has a width BS.

The width BS is preferably greater than 0.5mm, preferably greater than 1mm, and/or less than 8mm, preferably less than 5mm.

Fig. 6 shows a third embodiment of the main spring 9 according to the application in a schematic view. Fig. 7 shows a schematic front view of the main spring 9 according to fig. 6; fig. 8 shows a longitudinal section through the main spring 9 according to fig. 6; and fig. 9 shows an enlarged portion of the dot-dash line area of fig. 6.

The main spring 9 of the third embodiment differs from the first two embodiments in particular in that its circumferential web 9B changes its axial height position and/or its axial thickness in the circumferential direction about the spring axis B.

The axial height position preferably represents the axially highest point of the web 9B in the circumferential direction in an infinitely small web section.

Preferably, the axial height position of the web 9B is greatest and/or smallest in the region in which the support 9A is arranged in the direction of the supports 9C, 9D.

Preferably, the axial thickness of the web 9B is greatest and/or smallest in the region in which the support 9A is arranged in the direction of the support 9C, 9D. Preferably, the axial thickness of the web 9B is smallest in the region which is located exactly between the two regions of greatest axial thickness of the web 9B in the circumferential direction about the spring axis B.

Preferably, the axial thickness in the spring layer 9E runs from one of the legs 9A of the spring layer 9E to the adjacent leg 9A of the spring layer 9E as: thick-thin-thick. In particular, the axial thickness in the spring layer 9E with two brackets 9A runs: thick-thin-thick-thin, wherein the spring layer 9E takes turns on itself after the last "thin".

Preferably, the axial thickness of the web 9B is minimal in the region where the brackets 9A are provided above and/or below the web. Preferably, the axial thickness of the web 9B is smallest in the region which is located exactly between the two regions of greatest axial thickness of the web 9B in the circumferential direction about the spring axis B.

Preferably, the height H1 of the tab 9B is the axial spacing of the lowest point of the tab 9B from the highest point of the same tab 9B.

Preferably, the widths BS of the two brackets 9A of the two adjacent spring layers 9E are different. In particular, the width BS of the wider stent 9A is greater than 1.5 times the width BS of the narrower stent 9A.

The cross section of the connecting piece 9B is preferably at least substantially trapezoidal.

Fig. 10 shows a fourth embodiment of the main spring 9 according to the application in a schematic view. Fig. 11 shows a schematic front view of the main spring 9 according to fig. 10; and fig. 12 shows a partial enlargement of the area of the dash-dot line of fig. 10.

The main spring 9 of the fourth embodiment differs from the first three embodiments in that the carrier 9A transitions in a curved manner into the web 9B.

Preferably, the support 9A is rounded with a radius of curvature to the web 9B.

Preferably, in the region where the carrier 9A and the connecting piece 9B are connected to each other, one, preferably more, in particular all, of the outer surfaces of the carrier 9A and/or the connecting piece 9B are curved.

The outer surface of the carrier 9A or the connecting piece 9B is generally denoted in the present invention as the region on which no element is provided.

Preferably, the bracket 9A and the connecting piece 9B each meet each other with a radius of curvature of more than 1 mm.

Preferably, the bending of the support 9A and/or the connecting piece 9B does not change its direction or sign. Preferably, the cross section of the connecting piece 9B is at least substantially polygonal with oblique and/or rounded corners, in particular with four, five, six, seven, eight, nine or ten corners.

Preferably, the cross section of the bracket 9A is rectangular.

Fig. 13 shows a fifth embodiment of the main spring 9 according to the application in a schematic view. Fig. 14 shows a schematic longitudinal section through the main spring 9 according to fig. 13; and fig. 15 shows a partial enlargement of the dot-dash line area of fig. 13.

The fifth embodiment of the main spring 9 according to the application differs from the previous embodiments in that it does not have a support 9A, but rather is formed only by a web 9B.

The web 9B preferably changes its axial height position around the spring axis B, wherein preferably there is a longitudinal section of the main spring 9, which comprises in particular the spring axis B, in which the web 9B extends zigzag.

Preferably, the connecting piece 9B transitions to an adjacent connecting piece 9B.

Preferably, the spring layer 9E is formed by a connecting piece 9B.

Preferably, the height H1 of the connecting piece 9B is the same as the height of the spring layer 9E.

Preferably, the main extension plane of the spring layer 9E is inclined to the radial plane of the main spring 9 by an angle of in particular more than 5 °, preferably more than 10 °, and/or less than 40 °, preferably less than 30 °.

The axial thickness of the webs 9B is preferably constant in the circumferential direction, wherein this does not apply to the region where the two webs 9B meet each other.

Preferably, the cross section of the connecting piece 9B is at least substantially trapezoidal.

Preferably, the height H1 of the connecting piece 9B is given by the axial spacing between the two lowest points of two adjacent connecting pieces 9B. This is illustrated in fig. 14, in which the distance between two sections of two adjacent spring layers 9E is determined, the lowest point of the webs 9B being observed in each case.

Preferably, the angle enclosed by two adjacent webs 9B is greater than 10 °, preferably greater than 20 °, and/or less than 60 °, preferably less than 50 °.

Fig. 16 shows a sixth embodiment of the main spring 9 according to the application in a schematic view. Fig. 17 shows a schematic longitudinal section of the main spring 9 according to fig. 16.

The sixth embodiment of the main spring 9 according to the application differs from the already described embodiment in that the main spring is likewise formed only by the web 9B, which changes its axial height position in the circumferential direction, but the web 9B does not close onto itself after a complete rotation about the spring axis B, i.e. after a rotation of 360 °.

For simplicity of description, the main spring 9 of the sixth embodiment will be described as a coil spring. It is explicitly pointed out here that the main spring 9 of the sixth embodiment is not a coil spring, but rather is formed by a web 9B, which changes its axial height position in the circumferential direction, wherein the web 9B does not close onto itself after a complete rotation about the spring axis B, i.e. after a rotation of 360 °.

Preferably, the main spring 9 has a rise angle, a screw thickness WD, a screw width WB and a screw pitch HG.

Preferably, the pitch HG is greater than the screw thickness WD.

Preferably, the screw thickness WD is greater than 0.5mm, preferably greater than 1mm, and/or less than 5mm, preferably less than 4mm.

Preferably, the screw width WB is greater than 0.5mm, preferably greater than 1mm, and/or less than 5mm, preferably less than 4mm.

Preferably, the pitch HG is greater than 2mm, preferably greater than 3mm, and/or less than 20mm, preferably less than 15mm.

Preferably, the screw thickness WD is the axial height of the cross section of the spiral of the main spring 9 in this section.

Preferably, the cross section is rectangular, in particular square.

Preferably, the rising angle of the relaxed main spring 9 is greater than 5 °, preferably greater than 10 °, and/or less than 40 °, preferably less than 35 °.

The rising angle is preferably the angle at which the spring screw rises.

Preferably, the pitch HG is the sum of the screw thickness WD and the minimum axial spacing of the two cross sections of the spiral spring in a sectional front view, wherein the sectional plane contains the spring axis B.

The outlet spring 16 according to the application, which has been schematically illustrated in fig. 1, is further elucidated below, wherein the previous embodiments and aspects and features relating to the main spring 9 apply correspondingly or in addition, if not described in detail, and conversely, the following embodiments, illustrations and features relating to the outlet spring 16 apply correspondingly or in addition to different embodiments of the main spring 9.

Fig. 18 shows the outlet spring 16 in the corresponding state in a schematic view. Fig. 19 shows a schematic front view of the outlet spring 16 according to fig. 18 and fig. 20 shows a schematic longitudinal section of the outlet spring 16 according to fig. 18.

The characteristics already described above apply equally to the outlet spring 16.

Preferably, the outlet spring 16 has an outlet valve body 15, an upper support 16D, one or more webs 16B and/or one or more holders 16A and/or a spring shaft B.

Preferably, the geometric matrix formed by the outlet spring 16 is at least substantially frustoconical.

Preferably, the angle between the spring axis B and the generatrix of the truncated cone formed by the outlet spring 16 is greater than 1 °, preferably greater than 1.5 °, and/or less than 10 °, preferably less than 5 °.

The elastic section 16F preferably has a length L in the relaxed state of more than 5mm, preferably more than 10mm, and/or less than 50mm, preferably less than 40 mm.

The elastic section 16F preferably has a length LV of more than 4mm, preferably more than 8mm, and/or less than 40mm, preferably less than 32mm in the preloaded or mounted state.

Preferably, the elastic section 16F is compressed by more than 2%, preferably more than 3%, and/or less than 40%, preferably less than 35%, in the pre-tensioned or mounted state.

The elastic section 16F preferably has a length LV in the maximally compressed state of more than 3mm, preferably more than 7mm and/or less than 35mm, preferably less than 27 mm.

Preferably, the elastic section 16F is compressed by more than 3%, preferably more than 5%, and/or less than 60%, preferably less than 50% in the most compressed state.

Preferably, the outlet spring 16 is dimensioned such that the outlet valve 14 remains closed during (entire) movement of the pump piston 10 upwards or to the initial position, or during the entire filling of the pump chamber.

The outlet spring 16 is preferably likewise made of plastic, in particular a material mixture, as is the case for the main spring 9, particularly preferably of the same or the same material, as described below, or is produced therefrom.

Tests were performed with the outlet spring 16 proposed according to the application with respect to hysteresis, fatigue properties, force-displacement diagram and compression. The characteristics of the springs 9, 16 or the material mixture set forth below are therefore particularly preferred.

Preferably, the outlet spring 16 or the elastic section 16F is designed such that the characteristic value K1 is less than 0.05N/mm ^2.5, in particular less than 0.025N/mm ^2.5, and/or greater than 0.0005N/mm ^2.5, at least until a compression of 10% is achieved, wherein k1= (w·l ^0.5)/(V·S²), wherein W is the work performed to compress the outlet spring 16 from the relaxed state by the displacement S, L is the length of the elastic section 16F in the relaxed state, and V is the plastic volume of the elastic section 16F. Tests have surprisingly shown that the plastic springs thus constructed have very good fatigue resistance and/or can be compressed at least substantially reversibly.

Preferably, the characteristic value K1 is alternatively or additionally adapted to the main spring 9.

Preferably, the outlet spring 16 or the elastic section 16F is designed such that the characteristic value K2 is less than 0.005mm ^-3.5, in particular less than 0.0025mm ^-3.5, and/or greater than 0.00005mm ^-3.5, at least until a compression of 10%, wherein k2= (w·l ^0.5·RA)/(V·AF·E·S²), wherein W is the work done to compress the outlet spring 16 from the relaxed state by the displacement S, RA is the outer diameter of the elastic section 16F, AF is the filling coefficient of the relaxed elastic section 16F, E is the elastic modulus of the material of the elastic section 16F, and V is the plastic volume of the elastic section 16F. Tests have surprisingly shown that the plastic spring thus formed is at least substantially hysteresis-free and/or at least substantially has a linear force-displacement diagram.

Preferably, the characteristic value K2 is alternatively or additionally adapted to the main spring 9.

In the following table, characteristic values K1 and K2 and parameters determined experimentally for calculating K1 and K2 are shown for the outlet spring 16 according to the invention and the main spring 9 according to the invention. The main spring 9 is a first embodiment, wherein the characteristic values K1 and K2 preferably apply equally to other embodiments of the main spring 9. The springs 9 and 16 tested consist of plastic, i.e. a material mixture with 90% by weight of propylene and 10% by weight of polyethylene.

The work W is calculated by determining the displacement integral of the force along the compression displacement S.

Preferably, the plastic volume V of the elastic sections 9F, 16F is calculated by having a cross-sectional area of material from the axial beginning of the elastic sections 9F, 16F up to the axial end of the elastic sections 9F, 16F.

Preferably, the plastic volume V relates to the elastic section 9F in the relaxed state.

It is evident from the table and the following figures that the springs 9, 16, which meet the characteristic values K1 and K2, are at least substantially hysteresis-free, can be compressed at least substantially reversibly and/or have good fatigue resistance with respect to frequent compression or over a longer period of time.

Springs 9, 16 having different configurations with very similar characteristic values K1 and K2 (see table) can likewise be regarded as verification of characteristic values K1 and K2.

Fig. 21 is a force-displacement diagram of the detected outlet spring, in which the trends of the first compression LK1 and the first release LD1 and the tenth compression LK10 and the tenth release LD10 are shown. The compression displacement S of the outlet spring 16 is shown on the x-axis, while the return force F of the outlet spring 16 is shown on the y-axis in relation to the compression displacement S.

The test was carried out under practically applied test conditions, i.e. at room temperature of about 20 to 25 ℃ and at an air humidity of 50%.

It can be concluded from fig. 21 that the restoring force decreases from approximately 8.7N to 8.3N in the case of complete compression, i.e. only a very small decrease between the first and tenth compression or actuation.

From this map the following parameters can preferably be calculated.

The first compression required a work of 0.02175J, while the tenth compression required a work of 0.02075J.

The work released during the first release was 0.01985J, while in the case of the tenth release was 0.01900J.

Thus, the relative difference between the work required for the first/tenth compression and the work released for the first/tenth release is less than 30%. The spring is therefore at least substantially hysteresis-free.

Furthermore, the relative difference between the work required for the first compression and the tenth compression is less than 25%. The spring is thus at least substantially fatigue resistant.

Furthermore, the force-displacement diagram is quite linear, so that the elastic section 16F according to the invention has an at least substantially linear force-displacement diagram.

Furthermore, the figure shows that: the slope of the compression pattern LK1, LK10 or the release pattern LD1, LD10 varies by no more than 30% during compression or release.

Thus, the outlet spring 16 is at least substantially hysteresis-free, at least substantially reversibly compressible and has good fatigue resistance to frequent compression.

Preferably, the characteristic values K1 and/or K2 are suitable for the outlet spring 16 and/or the main spring 9.

Preferably, the main spring 9 of the first to sixth embodiments is intended to serve as a return element for the pump piston 10 and/or as an element for the inlet valve 11.

Preferably, the outlet spring 16 has a larger spring constant than the main spring 9.

Preferably, the outlet spring 16 is preset to serve as or form the valve body 15 of the outlet valve 14.

Fig. 22 shows a time curve or drop of the restoring force of the outlet spring 16, which is permanently preloaded or compressed by 3mm, the characteristic values of which are listed in the table.

The time in seconds is recorded on the x-axis and the return force F of the outlet spring 16 in newtons is recorded on the y-axis.

The test was carried out under practically applied test conditions, as in the case of determining charts and performing other tests and measurements according to fig. 21.

The graph shows that the return force of the outlet spring 16 decreases first and then gradually approaches a boundary value of about 50%. The return force of the outlet spring 16 drops by less than 50% in particular within 100 hours.

It can be seen here that: the outlet spring 16 has relatively good fatigue resistance to prolonged sustained, constant compression. Accordingly, the compressed springs 9, 16 of the output device 1 or of the pump 7 produce good stability or long-term storability.

The previous and subsequent embodiments with respect to the main spring 9 according to the application are correspondingly also applicable to the outlet spring 16 according to the application and vice versa, as already mentioned, so that in general only the spring 9 or 16 is referred to or referred to hereinafter.

The springs 9 and 16 are made of plastic or plastic.

Preferably, the plastic is a material mixture. Preferably, the material mixture comprises a base component and an additional component.

Preferably, at least 50% by weight and/or at most 95% by weight, in particular at most 90% by weight, of the material mixture is formed from the base component.

Preferably, the base component is formed from or made of polypropylene.

Preferably, the modulus of elasticity of the base component is greater than 1000MPa and/or the tensile limit of the base component is less than 1% until material breakage occurs.

Preferably, in order to determine the stretch limit until the material breaks, a cylindrical rod consisting of the material, 1cm in diameter and 10cm in length, is pulled apart by a force acting on its axial end along the longitudinal axis, and the relative length change at the time of material breaking defines the stretch limit.

Preferably, the density of the additional component or material mixture is equal to or less than 0.9g/cm ³.

Preferably, the modulus of elasticity of the additional component is less than 1000MPa and/or the tensile limit of the additional component until material breakage occurs is greater than 1%.

Preferably, the material mixture is formed from a thermoplastic and an elastomer.

Preferably, the additional component has polyethylene, an ethylene-octene copolymer as polyolefin elastomer and/or isotactic propylene repeating units with random ethylene distribution as polyolefin elastomer or is selected from among them.

Preferably, the modulus of elasticity of the material mixture is less than 1500MPa.

Preferably, the modulus of elasticity of the material mixture is non-linear with respect to the ratio of the portions of the base component or the additional component.

Preferably, the materials of the material mixture are made to be homogeneously physically mixed with each other, in particular by mechanical stirring, in particular before the springs 9, 16 are manufactured from the material mixture.

Preferably, the springs 9, 16 are manufactured by injection moulding. Other manufacturing variations are possible.

Preferably, the springs 9, 16 or the elastic sections 9F, 16F are designed such that they have no undercut on the injection tool side or from the outside, so that the injection tool can be removed after the plastic has solidified.

Preferably, the springs 9, 16 have a spring constant of less than 10N/mm, preferably less than 5N/mm, particularly preferably less than 2N/mm.

The load receiving (Lastenaufnahme) of the springs 9, 16 is optimized by means of biomimetic measures. Preferably, the webs 9B, 16B and the brackets 9A, 16A each meet each other with a radius of curvature of more than 1 mm. In this way an optimisation of the load distribution in the springs 9, 16 can be achieved. Plastic deformation of the springs 9, 16 in these areas is thereby avoided. This is solved by finite element computation. In particular, the springs 9, 16 can thereby be formed to be very material-saving.

Alternatively, the springs 9, 16 are caused to deform plastically during their first compression and to be compressed at least substantially reversibly during subsequent compression.

Preferably, the elastic sections 9F, 16F of the springs 9, 16 have a filling factor of more than 30%, in particular more than 50%, and/or less than 90%, in particular less than 80%.

The filling factor is generally expressed in the present invention as the ratio of the volume of material to the volume of the geometry formed by the elastic sections 9F, 16F, for example the volume of material V of the elastic sections 9F, 16F in the case of a hollow cylindrical spring 9, 16, compared to the volume of the hollow cylinder formed by the elastic sections 9F, 16F.

Preferably, the springs 9, 16 are designed as compression springs. In particular, the spring is therefore preferably not stretched or stretched beyond its relaxed state in its application.

Preferably, the spring axis B of the springs 9, 16 is at least substantially maintained under compression, preferably wherein this is achieved by means of the form of the springs 9, 16 and/or by mutually counteracting bending or tilting of the spring layer 9B and/or by means of external anti-bending means of the springs 9, 16 under compression of the springs 9, 16.

Preferably, if the output device 1 or the pump 7 is in the initial state and/or the springs 9, 16 are operated permanently in the compressed state, the springs 9, 16 are in a preloaded state.

Preferably, at the beginning of the operation of the output device 1 or the pump 7 or in order to compress the main spring 9, which is pre-stressed in particular in the initial state of the output device 1 or the pump 7, a starting actuating force F of less than 15N, preferably less than 10N, particularly preferably less than 5N, must be applied to the actuating element or the output head 4 of the output device 1 or the pump or to the main spring 9.

Preferably, the actuating force to be applied in order to achieve the final state of the output device 1 or in order to achieve the maximum compression of the main spring 9 is less than 50N, preferably less than 35N, particularly preferably less than 15N.

Preferably, the ratio between the restoring force of the main spring 9 in the maximally compressed state or final state of the output device 1 and the restoring force of the main spring 9 in the pretensioned state or initial state of the output device 1 is less than 6, preferably less than 4.

Preferably, the difference between the return force of the springs 9, 16 in the maximally compressed state and the return force of the springs 9, 16 in the minimally compressed state is less than 20N, preferably less than 15N, particularly preferably less than 10N.

Preferably, the springs 9, 16 are compressible without torsion.

A possible anti-torsion device for the springs 9, 16 can be realized in such a way that the radially protruding parts of the springs 9, 16 are introduced into one or more interspaces of the pump housing, which interspaces are preferably parallel to the spring axis B.

Preferably, the springs 9, 16 are formed in one piece with other components of the output device 1 or the pump 7, such as the outlet valve body 15. This enables a simple, cost-effective and compact construction of the output device 1 or of the pump 7.

The elastic section 9F preferably has a length LV in the pre-tensioned or installed state of more than 15mm, preferably more than 20mm, and/or less than 90mm, preferably less than 80 mm.

Preferably, the elastic section 9F is compressed by more than 2%, preferably more than 3%, and/or less than 40%, preferably less than 35%, in the pre-tensioned or mounted state.

The elastic section 9F preferably has a length LK in the maximally compressed state of more than 13mm, preferably more than 17mm, and/or less than 80mm, preferably less than 70 mm.

Preferably, the elastic section 9F is compressed by more than 3%, preferably more than 5%, and/or less than 60%, preferably less than 50% in the maximum compressed state.

The compression of the elastic section 9F is preferably derived by (1- ((L-S)/L)) · 100%, where L is the length of the elastic section 9F in the relaxed state and S is the compression displacement of the elastic section 9F.

As already mentioned, the springs 9, 16 according to the invention are preferably at least substantially hysteresis-free, fatigue-resistant, reversibly compressible, and/or the springs 9, 16 according to the invention preferably have at least substantially a linear force-displacement diagram.

Hysteresis of the springs 9, 16 is understood in the present invention as the difference between the compression and release characteristics of the springs. In particular, for springs 9, 16 with hysteresis, the work required to transform spring 9 from a relaxed state to a compressed state is greater than the work that would be released from that state if springs 9, 16 were released. In particular, in the force-displacement diagram of the spring 9 with hysteresis, the compression curve and the decompression curve do not overlap.

For at least substantially hysteresis-free springs 9, 16, the relative difference between the work required to transform the spring 9 from a relaxed state to a compressed state and the work released from that state when the springs 9, 16 are released is less than 30%, preferably less than 20%, particularly preferably less than 10%. In particular, the magnitude of the hysteresis depends on the compression strength of the springs 9, 16. The spring according to the invention is preferably hysteresis-free if the spring is compressed by less than 20%, preferably by less than 30%, particularly preferably by less than 40%.

Preferably, the springs 9, 16 are fatigue-resistant if the springs 9, 16 can be compressed more than 100 times, preferably more than 200 times, particularly preferably more than 500 times, to an extent of less than 20%, preferably less than 30%, particularly preferably less than 40%, without the spring constant of the springs 9, 16 decreasing and/or increasing by more than 30%. In particular, if the springs 9, 16 can be compressed to less than 20% for more than 1000 hours, preferably more than 5000 hours, particularly preferably more than 20000 hours, without the spring constant of the springs 9, 16 decreasing by more than 50%, the springs 9, 16 are fatigue-resistant.

By "reversibly compressible" is meant in the present invention generally that the springs 9, 16 have the same shape, relaxed length and/or spring constant before and after compression. In particular, if the relaxed length and/or the spring constant is only changed by less than 35% by compression, the springs 9, 16 can be compressed at least substantially reversibly. In particular, the springs 9, 16 according to the invention can be compressed at least substantially reversibly until less than 20%, preferably less than 30%, particularly preferably less than 40% of the compression.

If the restoring force of the springs 9, 16 is at least substantially proportional to the compression displacement of the springs 9, 16, the springs 9, 16 have an at least substantially linear force-displacement diagram. In particular, if the change in slope of the pattern in the force-displacement diagram is less than 30%, the force-displacement diagram is at least substantially linear. In particular, the force-displacement diagram of the springs 9, 16 according to the invention is at least substantially linear until the springs 9, 16 are compressed by less than 20%, preferably less than 30%, particularly preferably less than 40%.

A second embodiment of the outlet spring 16 is shown in fig. 23 and 24, which are described further below. The above description of the outlet spring 16 is preferably also applicable to the second embodiment, provided that some other details are not explicitly stated or that the foregoing description is clearly incompatible with the following description.

The embodiment of the outlet spring 16 shown in fig. 23 and 24 differs from the embodiment of the outlet spring 16 of fig. 18 to 20 in particular in the different forms of the spring element, which in the embodiment of the outlet spring 16 of fig. 18 to 20 is preferably formed by the web 16B and the carrier 16A.

In the embodiment shown in fig. 23 and 24, the outlet spring 16 preferably has a leaf spring or disk spring type construction.

Preferably, the outlet spring 16 has at least one, preferably at least two or more spring elements 19. The spring elements 19 are preferably arranged one after the other in the axial direction.

The spring elements 19 are preferably identically, in particular identically, constructed.

The spring elements 19 preferably each have or are formed from two identical, in particular identical and/or mirror-symmetrical sections 20. The section 20 preferably extends substantially transversely to the spring axis B of the outlet spring 16 in particular. Preferably, the section 20 is planar.

The spring element 19 and/or the section 20 preferably consist of plastic, in particular Polyethylene (PE) and/or polypropylene (PP), and/or an elastic material, respectively.

The sections 20 of the spring element 19 are preferably each formed and/or arranged mirror-symmetrically with respect to the mirror plane SE, preferably with the mirror plane SE extending in particular perpendicularly to the spring axis B. This is shown in particular in fig. 24.

The section 20 is preferably curved. In cross section, as shown in particular in fig. 24, the segments 20 preferably each form an arc, which is curved outwards from a (imaginary) plane arranged horizontally to the spring axis B.

The two sections 20 of the spring element 19 are preferably each bent in opposite directions, in particular simply and/or arcuately, in particular as shown in fig. 23 and 24. Preferably, the sections 20 each have a simply curved face, or the sections 20 each represent a simply curved portion. In particular, the two sections 20 of the spring element 19 each arch outward from the respective mirror surface SE, so that the distance between the two sections 20 of the spring element 19 decreases with increasing distance from the spring axis B.

Preferably, the two sections 20 of the spring element 19 are connected to one another at their ends spaced apart from the spring axis B in a direction transverse, in particular perpendicular, to the spring axis B. The spring element 19 is preferably formed in a ring shape.

The spring element 19 is preferably compressible. By bending the sections 20 in conjunction with the connected ends, in particular spring elements 19 are formed, which each have a free space 21 between the sections 20, which extends essentially transversely to the spring axis B. The free space 21 is mirrored in particular for the corresponding mirror surface SE of the spring element 19. Preferably, the free space 21 or the distance between the two sections 20 of the spring element 19 is greatest at the spring axis B and decreases with increasing distance from the spring axis B until the sections 20 come into contact with one another at the ends.

Preferably, the free space 21 enables compression or compaction of the outlet spring 16, in particular in combination with a plastic and/or elastic material of which the outlet spring 16 or the spring element 19 or the section 20 thereof is made. In the case of compression or compaction, the sections 20 of the spring element 19 preferably move toward one another and/or the free space 21 of the spring element 19 decreases.

Preferably, two adjacent spring elements 19 are each connected to one another by a connecting piece 22. The one or more connecting elements 22 are preferably made of the same material as the spring element 19 and/or are preferably formed in one piece with the spring element 19.

The connection 22 is preferably arranged in the region of the middle and/or spring axis B.

Preferably, the connecting element 22 is formed in an elongated and/or linear manner and/or extends transversely, in particular perpendicularly, to the spring axis B.

The sections 20 preferably each have an at least substantially constant thickness. The thickness of the segments 20 is preferably at least 0.2mm or more, preferably 0.4mm or more, and/or up to 0.8mm or less, preferably 0.6mm or less, in particular about 0.5mm.

The maximum distance between the two sections 20 of the spring element 19 or in particular the height of the free space 21 in the center or along the spring axis B and/or the section perpendicular to the mirror surface SE is preferably at least 0.75mm or more, preferably 0.85mm or more, and/or at most 1.15mm or less, preferably 1.05mm or less, in particular about 0.95mm.

The width of the free space 21, in particular, i.e. the length of the free space extending perpendicular to the spring axis B or parallel to and/or in the mirror surface SE, is preferably at least 3.0mm or more, preferably 3.5mm or more, and/or at most 5.0mm or less, preferably 4.5mm or less, in particular about 3.9mm.

The width of the connector 22 is preferably at least 0.6mm or more, preferably 0.7mm or more, and/or up to 1.0mm or less, preferably 0.9mm or less, in particular about 0.8mm.

The various aspects and features of the invention may be implemented independently of each other, but in any combination and/or order.

List of reference numerals:

1 output device

2 Product/fluid

3 Container

4 Output head

4A nozzle

5 Connecting piece

6 Shell parts

6A stop part

7 Pump

7A pump cavity

8 Pump housing

9 Main spring

9A bracket

9B connecting sheet

9C lower support

9D upper support

9E spring layer

9F elastic section

10 Pump piston

10A rod/section

11 Inlet valve

12 Inlet valve body

13 Inlet valve seat

14 Outlet valve

15 Outlet valve body

16 Outlet spring

16A bracket

16B connecting sheet

16D upper support

16E spring layer

16F elastic section

17 Rising pipeline

18 Outlet valve seat

19 Spring element

20 Sections

21 Free space

22 Connector

Axis of ordinates

B spring shaft

BS rack width

HG pitch

H1 Height of connecting piece

H2 Height of support

L relaxed spring length

LK minimum spring length

Spring length of LV pretension

Inner diameter of RI spring

RA spring outer diameter

S compression displacement

SE mirror surface

V Plastic volume

Width of WB screw

WD screw thickness.

Claims (19)

1. Springs (9, 16) made of plastic, in particular for a preferably manually operable output device (1),

The spring comprises an elastic section (9F, 16F) having a length L in a relaxed state,

It is characterized in that the method comprises the steps of,

The springs (9, 16) are configured in such a way that at least until 10% compression is achieved, the characteristic value K1 is less than 0.05[ n/mm2.5], where k1= (w·l0.5)/(v·s2), where W is the work done to compress the springs (9, 16) from a relaxed state by displacement S, and V is the plastic volume of the elastic sections (9F, 16F); and/or

The springs (9, 16) are configured in such a way that the characteristic value K2 is less than 0.005[ mm-3.5] until at least 10% compression, wherein k2= (w·l0.5·ra)/(v·af·e·s2), wherein W is the work done to compress the springs (9, 16) from a relaxed state by the displacement S, RA is the outer diameter of the elastic sections (9F, 16F), AF is the filling coefficient of the relaxed elastic sections (9F, 16F), E is the elastic modulus of the material of the elastic sections (9F, 16F), and V is the plastic volume of the elastic sections (9F, 16F); and/or

The elastic sections (9F, 16F) are reversibly compressible by at least 10% and the elastic modulus of the plastic is less than 1500MPa.

2. Springs (9, 16) made of plastic, in particular for a preferably manually operable output device (1),

The spring comprises an elastic section (9F, 16F) having a length L in a relaxed state,

It is characterized in that the method comprises the steps of,

The plastic is a material mixture with polypropylene as a basic component and at least one additional component,

Wherein the density of the plastic is equal to or less than 0.9g/cm ³; and/or

Wherein the density of the additional component is less than the density of the base component; and/or

Wherein the elastic modulus of the plastic is less than 1500MPa; and/or

Wherein the material mixture is formed from at least 50% by weight and a maximum of 95% by weight of the base component.

3. Spring according to claim 2, characterized in that the additional component has or is made of polyethylene, ethylene-octene copolymer and/or isotactic propylene repeating units with random ethylene distribution.

4. A spring according to claim 2 or 3, wherein the modulus of elasticity of the additional component is less than 1000MPa.

5. Spring according to one of claims 2 to 4, characterized in that the modulus of elasticity of the basic component is greater than 1000Mpa.

6. Spring according to one of claims 2 to 5, characterized in that the spring (9, 16) is constructed according to claim 1.

7. Spring according to one of the preceding claims, characterized in that the spring (9, 16) is manufactured by injection moulding.

8. Spring according to one of the preceding claims, characterized in that the spring (9, 16) has a spring constant of less than 10N/mm, preferably less than 5N/mm, particularly preferably less than 2N/mm.

9. Spring according to one of the preceding claims, characterized in that the elastic section (9F, 16F) has a filling factor of more than 15%, in particular more than 20%, and/or less than 90%, in particular less than 80%.

10. Spring according to one of the preceding claims, characterized in that the elastic section (9F, 16F) has a web (9B, 16B) extending at least substantially in the circumferential direction and a bracket (9A, 16A) extending at least substantially axially.

11. Spring according to claim 10, characterized in that the connecting piece (9B, 16B) and/or the bracket (9A, 16A) are arranged rotationally symmetrically with respect to the spring axis (B) of the elastic section (9F, 16F) and/or inversely symmetrically with respect to the middle point of the elastic section (9F, 16F) and/or mirror symmetrically with respect to a plane containing the spring axis (B) of the elastic section (9F, 16F).

12. Spring according to one of claims 8 to 11, characterized in that the ratio of the axial height H2 of the bracket (9A, 16A) to the axial height H1 of the connecting piece (9B, 16B) is greater than 1.2.

13. Spring according to one of claims 8 to 12, characterized in that the connecting piece (9B, 16B) and the bracket (9A, 16A) meet each other with a radius of curvature of more than 1mm, respectively.

14. Spring according to one of the preceding claims, characterized in that the ratio of the length L of the elastic section (9F, 16F) to the outer diameter RA of the elastic section (9F, 16F) is greater than 5.

15. Spring according to one of the preceding claims, characterized in that the ratio of the outer diameter RA of the elastic section (9F, 16F) to the inner diameter RI of the elastic section (9F, 16F) is greater than 1.2.

16. Spring according to one of the preceding claims, characterized in that the spring (9, 16) forms a valve member of the inlet or outlet valve (11, 14).

17. Output device (1), in particular for manual operation and/or for outputting a fluid (2), preferably a cosmetic product, comprising a pump (7) and a container (3) for said fluid (2),

Wherein the pump (7) has at least one spring (9, 16) made of plastic, in particular as a return element for the pump piston (10) and/or for the inlet valve (11) or the outlet valve (14), wherein the spring (9, 16) is preloaded or minimally compressed in the initial state of the output device (1) and maximally compressed in the final state of the output device (1),

It is characterized in that the method comprises the steps of,

The difference in the return force of the springs (9, 16) between the final and initial state is less than 20N, preferably less than 15N, particularly preferably less than 10N; and/or

-Said springs (9, 16) being compressed by at least 5% in said initial state and/or by less than 30% in said final state; and/or

The spring (9, 16) is constructed according to one of the preceding claims.

18. Output device according to claim 17, characterized in that the outlet spring (16) has a plurality of spring elements (19) arranged axially one after the other, wherein each spring element (19) has two curved sections (20) which are formed mirror-symmetrically to one another and are connected to one another at their ends.

19. The use of a spring (9, 16) made of plastic as a return element for a pump piston (10) and/or as a valve element for an inlet valve (11) or an outlet valve (14) of a particularly preferably manually operable output device (1) for outputting a fluid (2), preferably a cosmetic product,

It is characterized in that the method comprises the steps of,

Use of a spring (9, 16) according to one of claims 1 to 16, and in particular to install the spring (9, 16) in a pretensioned manner.