DE102022122501A1 - Valve of a compressor or pump - Google Patents

Abstract

The invention relates to a valve (11), having a valve opening (15) arranged between a fluid inlet (9) and a fluid outlet (10) through which a fluid can flow, as well as a sealing body (12) which can be moved by means of a fluid flow and the valve opening (15) covers in a closed position and releases in an open position, the sealing body (12) having an inflow side (16) pointing towards the valve opening (15) and an outflow side (17) pointing away from the valve opening (15), the inflow side (16 ) and the outflow side (17) are delimited by a common radial edge (18), the inflow side (16) having a central sealing surface (19) by means of which the valve opening (15) can be covered in the closed position, and in which in the Opening position of the sealing body (12), the radial edge (18) of which a fluid flow (L) can flow around. According to the invention, in order to extend the damage-free service life and reduce noise, it is provided that at least on the inflow side (16) of the sealing body (12) a plurality of flow-influencing elements ( 20a-20h) are arranged or designed.

Description

The invention relates to a valve, having a valve opening arranged between a fluid inlet and a fluid outlet through which a fluid can flow, and a sealing body which is movable by means of a fluid flow and covers the valve opening in a closed position and releases it in an open position, the sealing body being one for The inflow side has an inflow side facing the valve opening and an outflow side pointing away from the valve opening, the inflow side and the outflow side being delimited by a common radial edge, the inflow side having a central sealing surface by means of which the valve opening can be covered in the closed position and in the open position of the sealing body whose radial edge can be flowed around by a fluid flow. The invention also relates to a pneumatic compressor and a hydraulic pump with such a valve.

Such valves are used, for example, in piston compressors in compressed air supply systems in vehicles and are used to provide compressed air for many areas of application, including brake systems, air suspension systems, level control, clutch actuation and many more. What is important here are, among other things, the highest possible delivery rate, the lowest possible noise development, small dimensions, low manufacturing effort and high robustness. Such a valve can also be used with advantage on pumps by means of which a liquid can be conveyed. However, the structure and operation of such a valve will be largely explained below using pneumatic valves.

Piston compressors usually have a suction valve and a pressure valve, each with a valve seat, which is arranged between a cylinder housing with a piston arranged therein and a cylinder head. The piston is connected via a connecting rod to a drive shaft designed as a crankshaft. The cylinder head has an inlet chamber and an outlet chamber for air. The cylinder head is connected to the cylinder housing, for example, via the valve seats, to which the suction and pressure valves, which are usually designed as reed valves, are attached. The inlet chamber of the cylinder head is connected to the ambient air via a filter arrangement. During the intake stroke of the piston, it is connected to a working space of the cylinder housing via a valve opening through a then opened suction valve, usually designed as a plate valve or disk valve. During the ejection cycle of the piston, the working space of the cylinder housing is connected to the outlet chamber of the cylinder head via a further arranged valve opening through a then opened pressure valve, which is connected to a delivery line of the compressed air supply system. The suction valve in the form of a reed valve usually has an elastic, largely plate-shaped sealing body, the reed. During the intake cycle, the lamella lifts off from the associated valve seat in a pneumatically activated manner and releases the valve opening of the suction valve. During the exhaust cycle, the lamella of the suction valve lies sealingly against the valve seat.

Accordingly, the pressure valve has a further elastic, largely plate-shaped sealing body, i.e. a further lamella, which seals against the valve seat in the suction cycle and releases the associated valve opening of the pressure valve in a pneumatically activated manner in the exhaust cycle. Such lamellar sealing bodies have proven themselves many times over. They can be moved in a highly dynamic manner and therefore enable very short response times.

However, undesirable side effects are relatively often observed in compressors, such as valve rattling and the so-called coughing or howling of the compressor. It was recognized that these disturbing acoustic effects are correlated with strong pressure fluctuations in the air flow when flowing around the sealing bodies or when flowing around the slats when flowing through the valve openings. In addition to undesirable noise development, the durability of the sealing bodies or the slats can be reduced under unfavorable conditions. Chaotic fluid flows at the valve openings are also suspected of causing an undefined reduction in the actually expected delivery capacity of such compressors during the constantly changing cycle of the compressor.

In this area, a causality is assumed between the formation of eddies in the air flow when the air is sucked in or ejected in the compressor and the adverse effects described. If a body such as a reed valve is in a fluid flow in the compressor, relatively large individual vortices can periodically form behind the reed. This effect is known as the “Karman vortex street” and can lead to vortex-induced vibration excitation of the body surrounded by the flow. In the event of resonance, the body in question can even be damaged by strong vibrations.

The frequency of these air vortices is proportional to the so-called Reynolds number. The value of the Reynolds number depends on the density, viscosity and flow velocity of the fluid relative to a reference length of the body. For example, the flow around can be controlled with these parameters the lamella of a valve with a certain diameter can be described. The Reynolds number is a similarity number, which means that the change from a laminar to a turbulent flow occurs on geometrically similar bodies with the same Reynolds numbers. In a region of laminar flow boundary layers on the body, the Reynolds number is called subcritical; in a region of turbulent flow boundary layers, the Reynolds number is called supercritical.

It can now be assumed that the fluid flow at the valve openings and past the respective slats in the intake cycle and/or in the exhaust cycle of a compressor behaves supercritically, at least in sections and/or temporarily. This can then lead to the undesirable acoustic effects mentioned due to the flow vortices themselves, which generate a pulsating fluid flow. In particular, if the vortex generation matches a resonance frequency of system components along the fluid flow path, damage or increased wear on the valve can occur. The pressure differences created by the vortices lead to changing forces on the lamella, which then begins to wobble. This wobbling movement gives the lamella additional kinetic energy, which can lead to increased impact forces on the lamella and, as a result, to an undefined closing behavior on the valve seat. For example, the sound of a so-called whiplash of the lamella is heard when the valve in question closes. If the vibration of the lamella resonates with the exciting fluid flow, the lamella may even tear or break.

The one not pre-published DE 10 2022 113 977.8 the same applicant shows a pneumatic valve for a compressor with a valve opening through which flow can flow and a sealing body which is movable at the valve opening between an open position and a closed position and has two sides and an edge connecting the two sides. An inflow side is designed to cover the valve opening in the closed position. In the open position of the sealing body, the outflowing air can flow around its radial edge. The radial edge of the sealing body has a number of formations in the area of the flow-around section for scattering the fluid flow. These formations are aligned radially and, in one exemplary embodiment, also point away from the valve seat.

From the AT 295 018 B a plate valve for a piston compressor is known, with a valve seat and a valve plate for sealing flow channels arranged in the valve seat. The valve plate consists of a plurality of concentric rings which are connected to one another via radial webs. In addition, the valve plate has extensions that project freely beyond the sealing part of the plate edge. The extensions are formed on the outer circumference of the plate so that the extension surfaces of the valve plate first hit the valve seat when the valve is closed. The extensions give way elastically. This cushions the impact of the valve plate on the valve seat and protects the sealing part of the plate edge. Adverse flow eddies and the like, which can occur in the air flow when flowing through the channels in the valve seat, are not mentioned.

Against this background, the invention is based on the object of proposing a valve for pneumatic or hydraulic pumps which is operationally reliable and durable as well as low-noise in operation. In addition, adverse effects of a fluid flow on the valve when it is opened and closed should be avoided as far as possible. Such a valve should be suitable for use in piston compressors in compressed air supply systems in vehicles and for hydraulic pumps.

This problem is solved by a pneumatic valve with the features of claim 1, while advantageous refinements and developments of the invention are defined in the dependent claims.

The invention therefore relates to a valve, having a valve opening arranged between a fluid inlet and a fluid outlet through which a fluid can flow, and a sealing body which is movable by means of a fluid flow and covers the valve opening in a closed position and releases it in an open position, the sealing body being a inflow side pointing towards the valve opening and an outflow side pointing away from the valve opening, the inflow side and the outflow side being delimited by a common radial edge, the inflow side having a central sealing surface by means of which the valve opening can be covered in the closed position, and in which in the Opening position of the sealing body whose radial edge can be flowed around by a fluid flow.

To solve the problem, this valve provides that at least on the inflow side of the sealing body, a plurality of flow influencing elements are arranged or formed radially between its central sealing surface and its radial edge.

Particularly in pneumatic systems, such as piston compressors with pneumatic valves, dynamic pressure changes in an air flow lead to pressure surges or pressure hammers. Such a dynamic pressure change occurs when the valve is opened or closed quickly. To open or close the valve, the air must be accelerated or decelerated, which requires a certain force due to the inertia of the flow. This force results in a change in pressure and thus causes the pressure surge. Such pressure surges could only be avoided with infinitely slow opening and closing processes. Due to the response times required for the provision of compressed air in piston compressors for compressed air systems in vehicles, for example, pressure surges are unavoidable in real operation. The resulting pressure surge is passed on as a pressure wave, with excessive pressure surges causing damage to the affected pneumatic system. Furthermore, pressure surges can lead to an excitation of the pneumatic system or parts of it, which responds with a resonance oscillation at its natural frequency.

The invention was based on the knowledge that the acceleration of the air in the valve in question generates turbulent flows, which cause an excitation of the oscillatory components of a valve that flow around and thus cause a strong generation of noise. In particular, it is assumed that in an air flow that arises in the intake cycles and exhaust cycles within a compressor, individual large flow vortices can form from a laminar or turbulent flow, which are harmful to the mechanical integrity of the sensitive sealing body and the valve seats. These vortices are particularly pronounced and undesirable at the edge of the sealing body and in the area of the valve opening. Particularly affected by such turbulence is the sealing body that is movably accommodated in such a valve, which is arranged in the flow path of the fluid and thus flows directly around it. The opening or closing of the valve causes the pressure surge and due to the required mobility of the sealing body, it is particularly susceptible to being massively excited by the pressure surge and generating undesirable noise. This is where the invention comes into play to solve the problem.

The flow influencing elements arranged or designed according to the invention on the inflow side of the sealing body can prevent the formation of unfavorable large fluid eddies when passing through the valve through two mechanisms of action. On the one hand, the fluid flow leaving the valve opening is broken down into several small partial fluid flows on the inflow side of the sealing body. After leaving the sealing body, these partial fluid flows each form comparatively small flow vortices, which interfere with one another as the flow progresses and form a quasi-continuous fluid flow. This significantly reduces excessive pressure fluctuations at the valve openings. In any case, large individual vortices and periodic vortex sequences, such as those observed in a Karman vortex street and which are seen as a major cause of valve rattling and whiplash with premature wear of the valves in the compressor, are reliably avoided.

To produce a second mechanism of action, the flow influencing elements on the sealing body can also be designed and/or arranged in such a way that they are already close to the radial edge or exactly at the radial edge of the sealing body, i.e. before flow flows around it, on the inflow side of the sealing body form small flow vortices which, after leaving the sealing body, are not able to generate the described unfavorable sealing body movements due to their size, or even interfere with one another in a favorable flow pattern and thereby lose effectiveness.

By means of the flow influencing elements, it is achieved in particular that shock-like, violent impact movements of the sealing body when it is placed against the valve seat are avoided or at least weakened. The flow, which is virtually smoothed in this way, can also have an advantageous effect on the valve throughput and thus on the delivery capacity of the compressor. The risk of a sudden failure of the compressor due to a broken plate or a shortened maximum service life of the suction and pressure valves can be significantly reduced by using the invention.

In order to use the first mechanism of action according to a first development of the valve having the features of the invention, it is provided that the flow influencing elements are arranged and designed on the inflow side of the sealing body in such a way that by means of them a fluid flow passing through the valve opening and the sealing body before leaving the radial Edge of the sealing body can be divided into a plurality of partial fluid streams.

A second development of the valve having the features of the invention provides that the flow influencing elements are designed and arranged in such a way that small flow vortices can be generated in a targeted manner in a fluid flow passing through the valve opening and the sealing body.

Furthermore, it can be provided that the flow influencing elements are arranged or formed on the inflow side of the sealing body and additionally, overlapping the radial edge of the sealing body, on the outflow side

By means of flow influencing elements arranged or formed on the outflow side of the sealing body, the scattering of the fluid flow into partial fluid flows as it flows around the edge of the sealing body can be further intensified. After the fluid flow has passed the suction valve, undesirable formation or repeated formation of individual large vortices in the downstream compression space can be prevented even more reliably with the help of flow influencing elements arranged or formed on the outflow side of the sealing body. Accordingly, after the air flow has passed the pressure valve, undesirable formation or repeated re-formation of individual large vortices in the downstream area of the fluid outlet can be even better suppressed.

According to another development of the invention, it can be provided that flow influencing elements are arranged or formed on the inflow side of the sealing body and additionally on the valve opening. By means of flow influencing elements, which are arranged or formed in the area of the valve opening, an air flow passing through the valve opening can be divided even better into a plurality of turbulent partial fluid flows.

According to an advantageous embodiment of the valve having the features of the invention, it can be provided that the valve is a disk valve, the sealing body of which is designed as an elastic, largely plate-shaped and / or circular or annular disk. An elastic, largely plate-shaped sealing body of a pneumatic valve of a compressor, in the form of a thin disk or a thin plate, predominantly made of metal, is often referred to as a lamella, including here. The excessive pressure fluctuations already described due to the formation of vortices in a compressor have a particularly disadvantageous effect on the relatively sensitive elastic slats of a slat valve. By using the invention, these disadvantages can be largely avoided. The invention is therefore particularly advantageous for use on reed valves, but is not limited to this.

According to a further embodiment, it can be provided that the sealing body additionally has an elastic fastening arm of the same material. The sealing body can be easily attached to a fixed part of the compressor, for example to a cylinder head and/or to a cylinder housing of the compressor, by means of such an arm. Due to the identical material of the two parts, temperature-related and/or force-related or moment-related material tensions between the sealing body and the fastening arm can be avoided.

According to an alternative embodiment of the valve in question, it can be provided that it is designed as a check valve whose sealing body has a bell-like geometry. Accordingly, other valve shapes than reed valves in a compressor can advantageously have the features of the invention, such as a bell-shaped check valve, on the sealing body of which flow influencing elements are arranged or formed on the upstream side. These are suitable for breaking down the air flow passing through the valve opening into several interfering partial air flows in order to avoid the formation of individual large air vortices. For this purpose, the bell-like sealing body is designed, for example, in one section as a hollow body, the outer lateral surface of which forms an inflow side, and the inner lateral surface of which forms an outflow side. The flow influencing elements can be arranged or formed in particular on the inflow side between a central sealing surface of the sealing body of the check valve and the radial edge of the inflow side.

A further embodiment of the valve having the features of the invention provides that at least some of the flow influencing elements of the sealing body are designed as holes, the respective edge of which connects the inflow side and the outflow side of the sealing body with one another, with several of these hole-shaped flow influencing elements being formed close to the radial edge of the sealing body are without reaching it.

In this regard, it is defined that a flow influencing element formed radially between the central sealing surface and the radial edge of the sealing body is defined in the form of a hole by its hole edge, which connects the inflow side and the outflow side of the sealing body to one another. Accordingly, the sealing body can have holes without teeth being formed on the radial ends in this embodiment.

The holes are, for example, arranged at a distance from one another in such a way that they form a ring of holes. After leaving a valve opening, a fluid flow can therefore be partially guided through the holes mentioned, so that a number of partial fluid flows initially correlated with the number of holes is created. However, the holes at least enable partial pressure equalization between the two sides of the sealing body. The partial fluid flows will influence each other as the flow progresses, thereby avoiding the creation of a large flow vortex. In the case of a sealing body in the form of an elastic lamella, the holes in the edge area have the further advantage that the structure of the lamella is even more flexible than without such holes. This means that the impact of the lamella on the sealing seat of the valve is better cushioned and the valve is additionally protected.

The hole-shaped flow influencing elements can have a circular, station-shaped or elliptical geometry. Alternatively, other hole geometries can also be used. For example, it can be provided that the hole-shaped flow influencing elements have a ring segment-shaped geometry. The distance in the circumferential direction between two adjacent ring segment-shaped holes and the radial distance of these holes from the radially outer edge of the lamella can be dimensioned such that, on the one hand, the desired function of flow division and, on the other hand, the necessary rigidity of the structure of the lamella body when placed on the valve seat are advantageously coordinated with one another .

However, the hole-shaped flow influencing elements can also have a polygonal geometry with rounded corners, with notch stresses in the sealing body being avoided by means of the rounded corners.

In a further alternative embodiment, it can be provided that the hole-shaped flow influencing elements are designed as notch-shaped incisions in the sealing body, arranged radially away from the central sealing surface, without reaching its radial edge. Accordingly, a sealing body structured with notches can be advantageously used to achieve the desired division of the fluid flow. Taking into account the rigidity of the sealing body, a relatively large number of notches can be formed on the sealing body, whereby the fluid flow is divided into many small partial fluid flows as it passes through the valve opening. The flow generated in this way can have many small eddies, which at least partially interfere with each other, so that the formation of a large individual eddy is prevented.

According to another embodiment of the invention, it can be provided that at least some of the flow influencing elements are designed as guide fins, which have the geometry of a right-angled or similar triangle in the radial cross section and the geometry of a rectangle, a triangle or a trapezoid in the top view, with a first Side of the respective guide fin-shaped flow influencing elements is arranged flush with the radial edge of the sealing body and a second side of the respective guide fin lies flat on the inflow side and is firmly connected to it, and wherein several of these guide fin-shaped flow influencing elements are arranged along the radial edge of the sealing body.

Accordingly, instead of holes in the sealing body, a plurality of guide fin-shaped flow influencing elements can be formed or arranged on its inflow side along its radial edge, which extend axially and radially and towards the attacking fluid flow, so that the fluid flow after flowing through the valve opening by means of these guide fin-shaped flow influencing elements the sealing body is divided into several partial fluid flows. Such guide fin-shaped flow influencing elements arranged or designed on the inflow side of the sealing body have the advantage that, due to their arrangement, in comparison to holes or incisions in the sealing body, no notch effect occurs, which can place relatively strong stress on the material of the sealing body during operation of the compressor or pump.

The flow influencing elements can be designed as fins. Fin-like flow influencing elements are advantageously suitable for targeted guidance of the fluid flow in the area of the valve seat. The shape of the fins, viewed from above, can be designed in different ways, with rectangular, triangular or trapezoidal contours being considered advantageous. The more flow-efficient these fin-like flow influencing elements are, the more suitable they are for dividing the fluid flow coming from the area of the valve seat into several partial fluid flows. These partial fluid flows only form comparatively small flow vortices after leaving the sealing body. Fin-like flow influencing elements with a rather flow-unfavorable geometry, on the other hand, are used to generate comparatively small flow vortices directly on the sealing body or on the inflow side of the lamella.

According to another embodiment, it can therefore be provided that at least some of the flow influencing elements are designed as ring segment-shaped blocks which are formed on the inflow side of the sealing body or are firmly connected to it, with several of these block-shaped flow influencing elements being arranged along the radial edge of the sealing body.

By means of these block-shaped flow influencing elements, the fluid flow can be effectively disturbed in accordance with the invention when the flow passes the radial edge of the sealing body. From the flow at the valve opening, which can be laminar or already turbulent, a flow consisting of several turbulent partial fluid flows is then reliably generated. If the flow is still laminar when flowing towards the valve opening, the block-shaped flow influencing elements each advantageously have a turbulence-forming effect, in the sense that several smaller flow vortices are formed, but no large flow vortices. The creation of disadvantageous large flow eddies is then no longer possible. Thanks to a geometric circular segment shape, the blocks can be easily formed or arranged on the circumferential radial edge of the sealing body.

According to another embodiment of the invention, it can be provided that at least some of the flow influencing elements are designed as tunnels, and that these tunnel-shaped flow influencing elements each have the cross-sectional geometry of a hollow profile. Accordingly, the fluid flow can be divided by using tunnel-shaped flow influencing elements. At the tunnel exits and further downstream, the partial fluid flows interfere with one another, so that the formation of large flow eddies is advantageously prevented.

Furthermore, it can be provided that the tunnel-shaped flow-influencing elements each have the cross-sectional geometry of a semicircle, with these tunnel-shaped flow-influencing elements being arranged flat on the inflow side of the sealing body and firmly connected to it, with the tunnel-shaped flow-influencing elements on the inflow side starting radially away from the central sealing surface extend towards the radial edge of the sealing body, and wherein several of these tunnel-shaped flow influencing elements are arranged along the radial edge of the sealing body. The advantage here is that the partial fluid flows generated in the tunnel tubes are specifically directed radially outwards, where they are quickly diverted from the valve seat after emerging from the tunnel tubes.

According to a further embodiment of the invention, it can be provided that at least some of the flow influencing elements are designed as guide teeth, which are arranged or designed along the radial edge of the sealing body. Here, these guide tooth-shaped flow influencing elements form a plane at least in sections with the first sealing surface of the sealing body. Accordingly, the sealing body can be provided with teeth on its outer circumference. These teeth can, for example, be involute teeth or be designed with a sawtooth profile or a sinusoidal profile. A narrow tooth spacing with many small teeth is considered advantageous in order to achieve an effective division of the air flow into partial air flows with many small flow eddies.

According to another development of the invention, it can be provided that at least some of the flow influencing elements are designed as guide teeth, which are arranged or formed along the radial edge of the sealing body, these guide tooth-shaped flow influencing elements being designed to be curved at least in sections in the flow direction towards the outflow side of the sealing body. Because the flow influencing elements in the form of guide teeth are curved at least in sections in the flow direction of the fluids flowing past, the effectiveness of the division of the air flow into partial fluid flows can be further improved.

Another embodiment provides that the flow influencing elements are arranged or designed to be distributed equidistantly from one another on the radial edge of the sealing body over its circumference. The arrangement of the flow influencing elements between the sealing surface and the radial edge of the sealing body can be advantageously adapted to the geometric dimensions of the sealing body, the sealing surface and the flow influencing elements. Through an equidistant arrangement of the flow influencing elements, the fluid flow can be divided into partial fluid flows of approximately equal size.

According to an alternative embodiment of the invention, it can be provided that the flow influencing elements are arranged or designed on the radial edge of the sealing body so close to one another that they form a circumferential, at least largely continuous flow influencing edge. This flow influencing edge creates an at least largely closed edge or in the case of holes, an annular cutout is created close to the edge of the sealing body, on which a flow boundary layer can form. Such a flow guide edge can be suitable for suppressing the formation of large individual vortices in the fluid flowing past.

According to another alternative embodiment of the invention, it can be provided that several annular rows of flow influencing elements are arranged or formed in the radial direction between the central sealing surface and the radial edge of the sealing body. By means of several rows of flow influencing elements of the type described on the inflow side of the sealing body, the fluid flow impinging there is advantageously swirled, so that no large flow vortices arise downstream behind the sealing body.

The described embodiments can also be advantageously combined with one another. The invention is also not limited to the embodiments described. With knowledge of the invention, the person skilled in the art will find further flow influencing elements and their arrangement, which are suitable for dividing the fluid flow into partial fluid flows or for generating small flow eddies in the area of the inflow side of the sealing element in order to prevent the formation of large flow eddies and their described disadvantageous effect .

In summary, it can be said that the interfering partial fluid flows generated by the flow influencing elements form a rather undefined fluid flow overall after flowing through the valve opening. However, one can at least assume that the flow influencing elements destroy large flow vortices as they pass through the valve opening and the sealing body or suppress their formation from the outset. As a result, a possibly mechanically sensitive reed valve can be better protected from damage, undesirably loud noise and premature wear by the flow influencing elements according to the invention than before.

The invention further relates to a compressor with such a pneumatic valve. Such a compressor can, for example, be part of a compressed air supply system in a commercial vehicle. The compressor is then improved in terms of its noise, its delivery capacity and its service life using the features of the invention.

Finally, the invention relates to a hydraulic pump with a valve which has the features mentioned in at least one of the patent claims.

• 1 eine schematische Längsschnittansicht durch einen Kompressor mit einer ersten Ausführungsform eines pneumatischen Ventils gemäß der Erfindung,
• 2 einen teilweisen Querschnitt A-A durch einen Dichtkörper des Ventils gemäß 1,
• 3 den Dichtkörper des Ventils gemäß 1 und 2 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß einer ersten Ausführungsform,
• 4 den Dichtkörper gemäß 1 und 2 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß einer zweiten Ausführungsform,
• 5 den Dichtkörper gemäß 1 und 2 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß einer dritten Ausführungsform,
• 6 eine schematische Längsschnittansicht durch einen Kompressor mit einem pneumatischen Einlassventil gemäß einer vierten Ausführungsform,
• 7 einen teilweisen Querschnitt A-A durch einen Dichtkörper des Ventils gemäß 6,
• 8 den Dichtkörper gemäß 6 und 7 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß der vierten Ausführungsform,
• 9 den Dichtkörper gemäß 6 und 7 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß einer fünften Ausführungsform,
• 10 den Dichtkörper gemäß 6 und 7 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß der sechsten Ausführungsform,
• 11 einen teilweisen Querschnitt A-A durch einen Dichtkörper des Ventils mit Strömungsbeeinflussungselementen gemäß einer siebten Ausführungsform,
• 12 den Dichtkörper gemäß 11 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß der siebten Ausführungsform,
• 13 einen Dichtkörper des Ventils ähnlich dem der 11 in einer Draufsicht mit einem Strömungsbeeinflussungselemente gemäß einer achten Ausführungsform,
• 14 einen teilweisen Querschnitt A-A durch einen Dichtkörper eines Ventils mit Strömungsbeeinflussungselementen gemäß einer neunten Ausführungsform,
• 15 den Dichtkörper gemäß 14 in einer Draufsicht den mit Strömungsbeeinflussungselementen gemäß der neunten Ausführungsform,
• 16 einen teilweisen Querschnitt A-A durch einen Dichtkörper eines Ventils mit Strömungsbeeinflussungselementen gemäß einer zehnten Ausführungsform,
• 17 den Dichtkörper gemäß 16 in einer Draufsicht mit Strömungsbeeinflussungselementen gemäß der zehnten Ausführungsform,
• 18a eine zweite Ausführungsform eines pneumatischen Ventils mit einem glockenförmigen Dichtkörper in einem halben Längsmittenschnitt,
• 18b eine Ansicht des pneumatischen Ventils gemäß 18a mit Blickrichtung vom Ventilsitz zur Dichtfläche des glockenförmigen Dichtkörpers,
• 19a einen halben Längsmittenschnitt wie der gemäß 18a, jedoch durch ein bekanntes pneumatisches Ventil mit einem glockenförmigen Dichtkörper, sowie
• 19b eine Ansicht des bekannten pneumatischen Ventils gemäß 19a mit Blickrichtung vom Ventilsitz zur Dichtfläche des glockenförmigen Dichtkörpers.

The invention is explained in more detail below using some exemplary embodiments shown in the accompanying drawing. These exemplary embodiments are explained using a compressor for compressing air, although the same valve can also be used on a hydraulic pump for conveying a liquid. Shown in the drawing

• 1 a schematic longitudinal sectional view through a compressor with a first embodiment of a pneumatic valve according to the invention,
• 2 a partial cross section AA through a sealing body of the valve 1 ,
• 3 the sealing body of the valve accordingly 1 and 2 in a top view with flow influencing elements according to a first embodiment,
• 4 the sealing body accordingly 1 and 2 in a top view with flow influencing elements according to a second embodiment,
• 5 the sealing body accordingly 1 and 2 in a top view with flow influencing elements according to a third embodiment,
• 6 a schematic longitudinal section view through a compressor with a pneumatic inlet valve according to a fourth embodiment,
• 7 a partial cross section AA through a sealing body of the valve 6 ,
• 8th the sealing body accordingly 6 and 7 in a top view with flow influencing elements according to the fourth embodiment,
• 9 the sealing body accordingly 6 and 7 in a top view with flow influencing elements according to a fifth embodiment,
• 10 the sealing body accordingly 6 and 7 in a top view with flow influencing elements according to the sixth embodiment,
• 11 a partial cross section AA through a sealing body of the valve with flow influencing elements according to a seventh embodiment,
• 12 the sealing body accordingly 11 in a top view with flow influencing elements according to the seventh embodiment,
• 13 a sealing body of the valve similar to that of the 11 in a top view with a flow influencing element according to an eighth embodiment,
• 14 a partial cross section AA through a sealing body of a valve with flow influencing elements according to a ninth embodiment,
• 15 the sealing body accordingly 14 in a top view of the flow influencing elements according to the ninth embodiment,
• 16 a partial cross section AA through a sealing body of a valve with flow influencing elements according to a tenth embodiment,
• 17 the sealing body accordingly 16 in a top view with flow influencing elements according to the tenth embodiment,
• 18a a second embodiment of a pneumatic valve with a bell-shaped sealing body in a half longitudinal center section,
• 18b a view of the pneumatic valve according to 18a looking from the valve seat to the sealing surface of the bell-shaped sealing body,
• 19a half a longitudinal center cut like that shown 18a , but by a known pneumatic valve with a bell-shaped sealing body, as well
• 19b a view of the known pneumatic valve according to 19a looking from the valve seat to the sealing surface of the bell-shaped sealing body.

Some components in the figures match, so they are labeled with the same reference numbers.

Accordingly, the shows 1 a compressor 1 in the design of a piston compressor, which is integrated, for example, in a compressed air supply system, not shown, of a vehicle. The compressor 1 has a cylinder housing 2 with a piston 3 arranged therein. A cylinder head 6 is connected to the cylinder housing 2. The piston 3 divides an interior of the cylinder housing 2 into a compression space 4 and a neutral space 5. In the 1 the compression space 4 is formed above and the neutral space 5 below the piston 3. For pneumatic separation of the compression space 4 from the neutral space, the piston 3 has an undesignated circumferential seal. On the side of the piston 3 facing away from the compression space 4, there is a crankcase 7 of the compressor 1 below the neutral space 5. The interior of the crankcase 7 is connected to the neutral space 5, so that the same air pressure prevails in the neutral space 5 as inside the crankcase 7. The Neutral space 5 can also be part of the interior of the crankcase 7. The piston 3 is connected in a known manner via a connecting rod 8 to a drive shaft designed as a crankshaft and not shown here.

By rotating the drive shaft, the piston 3 is moved upwards or downwards by means of the connecting rod 8. A downward movement corresponds to an intake stroke of the compressor 1, in which the compression space 4 is enlarged. In the in 1 In the operating situation shown, the compressor 1 is currently in the intake cycle. During the intake stroke, as a result of a negative pressure created in the compression space 4, an inlet-side first pneumatic valve 11 of the compressor 1, which acts as a suction valve, opens. As a result, ambient air flows into the compression space 4 via a fluid inlet 9 of the compressor 1 that is connected to the surrounding atmosphere. During an upward movement of the piston 3, which corresponds to a compression phase, the piston 3 reduces the volume of the compression space 4. The air in the compression space 4 is thereby compressed, which leads to an increase in pressure in the compression space 4. This closes the first pneumatic valve 11 on the inlet side. The pressure in the compression chamber 4 continues to increase until either a second pneumatic valve 35 of the compressor 1 on the outlet side, which acts as a pressure valve, opens or the piston 3 reaches its top dead center. The outlet-side second pneumatic valve 35 opens when the pressure in the compression chamber 4 exceeds the pressure in the area of a fluid outlet 10 of the compressor 1. The fluid outlet 10 of the compressor 1 is connected via a compressed air line, not shown, to further elements of the compressed air supply system mentioned, in particular to at least one compressed air storage and compressed air consumers.

The two pneumatic valves 11, 35, i.e. the suction valve and the pressure valve, are largely identical in construction, so that the following description is limited to one of the two valves, here for example to the first pneumatic valve 11 on the inlet side.

According to a first embodiment, the first pneumatic valve 11 is designed as a plate-shaped reed valve, which is shown in various embodiments in FIGS 1 to 17 is shown.

Like in the 1 to 3 can be seen more clearly, the pneumatic valve 11 in the design of a reed valve consists of a sealing body 12 in the form of an elastic circular lamella and an elastic fastening arm 13. The sealing body 12 and the fastening arm 13 are connected to one another in one piece and made of the same material and are made, for example, from a metal. As the 1 shows, the fastening arm 13 of the sealing body 12 is arranged with its free end between the cylinder housing 2 and the cylinder head 6 and fastened there, for example by means of a clamp connection. At its other end, the fastening arm 13 is, as mentioned, connected to the sealing body 12, so that the sealing body 12 is elastically movable by means of an air flow or by a negative pressure. The circular sealing body 12 in this case is arranged immediately adjacent to an associated valve seat 14. In the present case, the valve seat 14 is designed as a step-shaped extension of a cylindrical valve opening 15 formed in the cylinder head 6, extending in the direction of the sealing body 12. The valve seat can also simply be formed by an associated circular flat surface of the cylinder head.

As in the cross section AA through the sealing body 12 according to 2 can be seen more clearly, the sealing body 12 has an inflow side 16 pointing towards the valve opening 15 and an outflow side 17 pointing away from the valve opening 15. The inflow side 16 and the outflow side 17 are limited by a common radial edge 18. The radial edge 18 is according to the exemplary embodiment 1 and 2 largely circular and with a smooth surface. The inflow side 16 has a central and circular sealing surface 19, which is designed to cover the valve opening in a closed position, the sealing surface 19 abutting the valve seat 14 in a sealing manner in a radially outer region 19a.

In the in 1 In the opening position of the sealing body 12 shown, an air flow generated by the movement of the piston 3 can flow around its radial edge 18. During the intake cycle of the compressor 1, air is sucked in from the environment via the fluid inlet 9 and through the valve opening 15. The suction generated pushes the pneumatic valve away from the valve seat 14, so that a strong air flow acts on the radial edge 18 of the sealing body 12 of the valve 11.

In order to prevent the lamellar sealing body 12 from striking the valve seat 14 in a whip-like manner during the following discharge cycle of the compressor 1, for which individual large flow vortices are viewed as a significant cause or at least as disadvantageously reinforcing, according to the invention at least on the inflow side 16 of the sealing body 12 A plurality of flow influencing elements are arranged or formed radially between the central sealing surface 19 and the radial edge 18 of the sealing body 12. The flow influencing elements are intended to avoid, as far as possible, the unwanted, noisy “valve whipping” as well as comparatively rapid valve wear and/or a reduced delivery capacity of the compressor 1 by influencing the air flow.

Some exemplary embodiments of such flow influencing elements on sealing bodies designed according to the invention are presented below. The description applies accordingly to the second pneumatic valve 35, which acts as a pressure valve of the compressor 1 during its discharge cycle. It therefore also has a lamellar sealing body with the features of the invention and is arranged on a second valve seat 36 with a second valve opening 37.

Accordingly, the in 3 Sealing body 12 of the pneumatic valve 11 shown in a plan view has first flow influencing elements 20a to 20h designed as holes, which are arranged along the radial edge 18 of the sealing body 12 at a short distance from it and at approximately the same distance from one another. In this exemplary embodiment, the flow influencing elements 20a to 20h have a circular geometry, as can be clearly seen in the top view.

According to a modification of this sealing body 12 and other sealing bodies according to 1 to 5 It can be provided that flow influencing elements which penetrate the sealing body 12 are only formed in the region of the sealing body 12 remote from the arm, i.e. not close to the fastening arm 13. This is in the 3 illustrated by the flow influencing elements 20d, 20e, 20f drawn with a dashed line. This avoids a possible weakening of the connection area between the sealing body 12 and the fastening arm 13.

The 3 also shows that, viewed in the circumferential direction, a partial fluid flow T1, T2 is formed between the hole-shaped flow influencing elements 20a, 20b, 20c, 20g, 20h there, which flow around the radial edge 18 of the sealing body 12 towards its outflow side 17, in order to compare there to form small flow vortices. For reasons of space, only two of these partial fluid flows are provided with reference numbers.

In 3 It can also be seen from flow arrows (not further designated) that a small part of the air flow L striking the central sealing surface 19 of the sealing body 12 flows out through the hole-shaped flow influencing elements 20a, 20b, 20c, 20g, 20h in the direction of the outflow side 17 of the sealing body 12. When they emerge from the hole-shaped flow influencing elements 20a, 20b, 20c, 20g, 20h, very small flow eddies arise, which also help to prevent the formation of large flow eddies T0 downstream behind the sealing body 12.

4 shows a second exemplary embodiment, in which the sealing body 12 of the pneumatic valve 11 has eight second flow influencing elements 21a to 21h designed as holes, which are also arranged along the radial edge 18 of the sealing body 12 at a short distance from it and at approximately the same distance from one another are, but have a ring segment-shaped geometry. The geometry of these hole-like flow influencing elements 21a to 21h can also be described as square with rounded corners.

5 shows a third exemplary embodiment in which the sealing body 12 of the valve 11 has twelve third flow influencing elements 22a to 22l designed as holes, which are also arranged along the radial edge 18 of the sealing body 12 at a short distance from it and at approximately the same distance from one another, but have a notch-shaped geometry.

The holes mentioned therefore form a first group of flow influencing elements 20a to 20h; 21 a.m. to 9 p.m.; 22a to 22l, the commonality of which is that their respective hole edge connects the inflow side 16 and the outflow side 17 of the sealing body 12 with each other. With these flow influencing elements 20a to 20h; 21 a.m. to 9 p.m.; 22a to 22l, part of the fluid flowing over the inflow surface 16 of the sealing body 12 can flow through the sealing body 12 to its outflow side 17. When leaving these flow influencing elements 20a to 20h; 9pm to 9pm; 22a to 22l on the outflow side 17 of the sealing body 12 then form very small flow vortices. At least these hole-shaped flow influencing elements 20a to 20h; 9pm to 9pm; 22a to 22l a pressure equalization takes place between the inflow side 16 and the outflow side 17 of the sealing body 12, which inevitably generates small fluid flows and makes the formation of large flow vortices more difficult or even prevents it. Between the hole-shaped flow influencing elements 20a to 20h; 9pm to 9pm; 22a to 22l, due to their disruptive effect, air can flow in partial fluid streams T1, T2 to the respective radial edge 18 of the sealing body 12, and flow around it towards its outflow side 17. These partial fluid flows T1, T2 then only advantageously form small flow vortices, which mechanically relieve the valve of the load in accordance with the task.

In a second group of flow influencing elements, a structure is formed with several individual parts fixedly arranged on the inflow side 16 of the sealing body 12. Accordingly, the shows 6 the compressor 1 with the pneumatic valve 11, for example with a type of flow influencing elements that belong to the second group mentioned.

As the 6 as well as the sectional view according to 7 show in more detail, these flow influencing elements 23a to 23p extend out of the plane of the inflow side 16 of the sealing body 12 in the direction of the valve opening 15. The 6 and the 7 as well as the top view in 8th show an example of a fourth exemplary embodiment, in which the sealing body 12 of the pneumatic valve 11 has sixteen fourth flow influencing elements 23a to 23p designed as guide fins, which are arranged at a distance from one another along the edge 18 of the sealing body 12. As in the cross-sectional view of the 7 As can be seen, these fourth flow influencing elements 23a to 23p each form a right-angled triangle in cross section, with a first side 24 of the respective guide fin being arranged flush with the radial edge of the sealing body 12, and a second side 25 of the respective guide fin being flat on the inflow side 16 of the sealing body 12 rests and is firmly connected to it.

In the 7 the flow influencing element 23a is shown in the variant in which it is formed on the inflow side 16 and across the radial edge 18 of the sealing body 12 and also on its outflow side 17.

According to the in the 8th Illustrated top view of this sealing body 12, the fourth flow influencing elements 23a to 23p are rectangular.

9 shows a fifth exemplary embodiment of flow influencing elements 26a to 26p, which belong to the second group mentioned. Here, the sealing body 12 has sixteen fifth flow influencing elements 26a to 26p, which are also designed as guide fins and are arranged at a distance from one another along the edge 18 of the sealing body 12. These fifth flow influencing elements 26a to 26p are, like the top view of the sealing body 12 according to 9 shows, triangular in longitudinal section. The tip of these flow influencing elements 26a to 26p points radially inwards towards the central sealing surface 19 of the sealing body 12. Since these flow influencing elements 26a to 26p are designed to be very streamlined, they are particularly suitable for dividing the air flow hitting the central sealing surface 19 of the sealing body 12 into several partial air flows T1, T2. After flowing around the sealing body 12, these partial air flows form the desired comparatively small flow vortices.

10 shows a sixth exemplary embodiment from the second group of flow influencing elements. Here, the sealing body 12 has sixteen sixth flow influencing elements 27a to 27p, which are also designed as guide fins and are arranged at a distance from one another along the edge 18 of the sealing body 12. The sixth flow influencing elements 27a to 27p are as shown in the top view 10 shows, trapezoidal in longitudinal section. The short radial side of these flow influencing elements 27a to 27p points radially inwards towards the central sealing surface 19 of the sealing body 12. Because of their geometry, these sixth flow influencing elements 27a to 27p are also quite suitable for dividing the flow impinging on the central sealing surface 19 of the sealing body 12 Air flow into several partial air flows T1, T2. However, due to their flattened inflow surface, which is formed radially on the inside, these cause the formation of small flow eddies in the area of the inflow side 16 of the sealing body 12, which prevent or at least make it difficult for comparatively large flow eddies to form after the flow has flowed around the sealing body 12.

The 11 and 12 show a seventh exemplary embodiment from the second group of flow influencing elements, in which the sealing body 12 has eight seventh flow influencing elements 28a to 28h, which are designed as blocks and are arranged along the radial edge 18 of the sealing body 12 at a distance from this edge and from one another. The seventh flow influencing elements 28a to 28h are according to 11 rectangular in cross section through the sealing body 12 and in the top view of the sealing body 12 according to 12 designed in the shape of a segment of a circle. These seventh flow influencing elements 28a to 28h according to 11 and 12 are similar to the sixth flow influencing elements 27a to 27p because of their trapezoidal geometry 10 . However, the seventh flow influencing elements 28a to 28h are suitable for generating a smaller number of partial fluid flows and the formation of flow vortices in the area of the inflow surface 16 of the sealing body 12 because of their larger circumferential length, their greater distance from one another and because of a comparatively smaller number avoid.

The 13 shows an eighth exemplary embodiment of flow influencing elements, in which the sealing body 12 has a single eighth flow influencing element 29. This eighth flow influencing element 29 forms a circumferential, but somewhat raised and closed flow guide edge close to the radial edge 18 of the sealing body 12. This flow guide edge can be arranged or designed as a one-piece ring element on the inflow side 16 of the sealing body 12, or can consist of a spaceless series of individual flow influencing elements of the type of the seventh flow influencing elements 28a to 28h. This eighth flow influencing element 29 ensures that at least one air vortex is created on the inflow side 16 of the sealing body 12, and not disadvantageously only downstream behind the outflow side 17 of the sealing body 12.

The 14 and 15 show a ninth exemplary embodiment from the second group of flow influencing elements, in which the sealing body 12 has sixteen ninth flow influencing elements 30a to 30p, which are designed as guide tunnels. These tunnel-shaped flow influencing elements 30a to 30p are arranged at a distance from one another along the radial edge 18 of the sealing body 12. The free radial end of this guide tunnel is arranged flush with the radial edge 18 of the sealing body 12. In the present case, these flow influencing elements 30a to 30p are semicircular in cross section, which is in the 14 can be seen in a flow influencing element 30e, which is additionally shown as an example outside the cross section AA. The tunnel-shaped flow-influencing elements 30a to 30p therefore each extend radially away from the radially outer region of the sealing surface 19a of the sealing body 12 up to its radial edge 18. After the flow through the tunnel-shaped flow-influencing elements 30a to 30p, a comparatively small air vortex forms at their exit formed, which flows to the outflow side 17 of the closing body 12. The space kept free between the tunnel-shaped flow influencing elements 30a to 30p serves to generate a partial fluid flow T1, T2, which flow around the closing body 12 in the direction of its outflow side 17. This Partial fluid flows T1, T2 also advantageously generate small flow vortices after flowing around the radial edge 18 of the sealing body 12.

The 16 and 17 show a tenth exemplary embodiment of flow influencing elements on the sealing body 12 of the first pneumatic valve 11 designed as a reed valve. Here, the sealing body 12 has an edge 31 instead of the previously smooth radial edge 18, which is formed by a plurality of teeth. Accordingly, this sealing body 12 has a plurality of tenth flow influencing elements 32 in the form of teeth. In the present example, the flow influencing elements 32 have a jagged profile, with the respective tooth base 33 connecting the inflow side 16 and the outflow side 17 of the sealing body 12 to one another.

So far, various embodiments of a first pneumatic valve 11 acting as a suction valve of a compressor 1 or of an identical second pneumatic valve 35 acting as a pressure valve in the form of a reed valve according to the 1 to 17 described.

An alternative design of a pneumatic valve 40 with a sealing body 41 having a flow influencing element 49 is described below, which also has the features of the invention. Accordingly, they show 18a and 18b an embodiment of a pneumatic valve 40 in the form of a check valve. This pneumatic valve 40 can be installed and effective, for example, as a suction valve or as a pressure valve in the compressor 1 or as an additional check valve or reducing valve in an associated channel in the compressor 1 or in another air compression system.

This pneumatic valve 40 has according to the 18a and 18a a bell-shaped geometry, with a sealing body 41, which has a base body 41a, which is surrounded by a bell-shaped hollow jacket 42. The hollow jacket 42 has an inflow side 43 facing away from the base body 41a and an outflow side 44 facing the base body 41a. The inflow side 43 merges into an associated frontal central sealing surface 45, with which the sealing body 41 lies sealingly against a valve seat 46 in a closed position in order to cover a valve opening 47. The free end of the hollow jacket 42 forms a radial edge 48 of the hollow jacket 42 or of the sealing body 41. The valve 40 has a non-shown, for example spring-operated, non-return mechanism of a known design, which keeps the valve 40 closed in a blocking position, and which is operated by a pneumatic Pressurization can be opened in one flow direction. According to the invention, on the inflow side 43 of the hollow jacket 42 of the sealing body 41, several eleventh flow influencing elements 49 in the form of guide blocks are arranged in two rows spaced apart from one another in the axial direction. Like the top view of this sealing body 41 from the direction of the valve seat 46 18b shows, these cuboid flow influencing elements 49 are arranged in two annular rows between the central sealing surface 45 and the radial edge 48 of the hollow jacket 42 of the sealing body 41.

For comparison show the 19b and 19b a valve 40* according to the prior art, which is largely identical in terms of its basic elements. In this valve 40*, no flow influencing elements are arranged on the radially outer cover surface 43* of the hollow jacket 42* of the sealing body 41* there.

In the intake stroke with the valve 40 open, in this embodiment according to the invention, an air flow L first passes through the valve opening 47 and then flows over the inflow side 43 of the sealing body 41, which is equipped with the cuboid flow-influencing elements 49. The air flow L is divided into several partial air flows TW1, TW2 by the flow-influencing elements 49 and swirled in such a way that small flow vortices TB1, ZB2 arise in the partial air flows TW1, TW2. In comparison, the conventional valve 40* according to 19a Due to the air flow L after passing through the valve seat 46*, the sealing surface 45* and the inflow side 43* of the sealing body 41*, a disadvantageously large flow vortex TB0 is only generated downstream behind the sealing body 41*. As the 18b shows, the arrangement and / or design of flow influencing elements 49 on the sealing body 41 is clearly suitable for advantageously breaking down an air flow L into several partial air flows TW1, TW2, in which comparatively small flow vortices TB1, TB2 or turbulence arise even in the area of the sealing body 41 . This creates the advantageous effects described.

List of reference symbols (part of the description)

1

compressor

2

Cylinder housing

3

Pistons

4

Compression space

5

Neutral space

6

cylinder head

7

crankcase

8th

connecting rod

9

Fluid inlet

10

Fluid outlet

11

First pneumatic valve, suction valve (first embodiment)

12

Sealing body on the first valve 11 (first embodiment)

13

Fastening arm on valve 11 (first embodiment)

14

Valve seat on compressor 1 (first embodiment)

15

Valve opening on compressor 1 (first embodiment)

16

Inflow side on the sealing body 12 (first embodiment)

17

Outflow side on the sealing body 12 (first embodiment)

18

First radial edge of the sealing body 12 (first embodiment)

19

Central sealing surface on the sealing body 12 (first embodiment)

19a

Radial outer area of the sealing surface 19

8pm - 8pm

First flow influencing elements, holes (first embodiment)

21a - 9pm

Second flow influencing elements, holes (second embodiment)

22a - 22l

Third flow influencing elements holes (third embodiment)

23a - 23p

Fourth flow influencing elements, guide fins (fourth embodiment)

24

First side of a flow influencing element 23a - 23p

25

Second side of a flow influencing element 23a - 23p

26a - 26p

Fifth flow influencing elements, guide fins (fifth embodiment)

27a - 27p

Sixth flow influencing elements, guide fins (sixth embodiment)

28a - 28h

Seventh flow influencing elements, blocks (seventh embodiment)

29

Eighth flow influencing element, flow guide edge (eighth embodiment)

30a - 30p

Ninth flow influencing elements, tunnels (ninth embodiment)

31

Second radial edge on the sealing body 12 (second embodiment)

32

Tenth flow influencing elements, teeth (tenth embodiment)

33

Tooth base of the sealing body (tenth embodiment)

35

Second pneumatic valve, pressure valve (first embodiment)

36

Second valve seat on compressor 1 (first embodiment)

37

Second valve opening on compressor 1 (first embodiment)

40

Pneumatic valve (second embodiment)

40*

Well-known pneumatic valve

41

Sealing body on valve 40 (second embodiment)

41*

Sealing body on the well-known valve 40*

41a

Base body of the sealing body 41 (second embodiment)

42

Hollow jacket on the sealing body 41 (second embodiment)

42*

Hollow jacket of the known sealing body 41*

43

Inflow side on the sealing body 41 (second embodiment)

43*

Inflow side on the known sealing body 41*

44

Outflow side on the sealing body 41 (second embodiment)

45

Central sealing surface on the sealing body 41 (second embodiment)

45*

Central sealing surface on the known sealing body 41*

46

Valve seat on the pneumatic valve 40 (second embodiment)

46*

Valve seat on the known valve 40*

47

Valve opening of the pneumatic valve 40 (second embodiment)

48

Radial edge on the sealing body 41 (third embodiment)

49

Eleventh flow influencing elements, cuboid (eleventh embodiment)

L

Fluid flow, air flow

T1

First part- air flow

T2

Second part- air flow

TF1

First partial air flow (with flow vortex)

TF2

Second part air flow (with flow vortex)

TB0

Large current vortex

TB1

First small current vortex

TB2

Second small flow vortex

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 1020221139778 [0009]
• AT 295018 B [0010]

Claims (24)

Valve (11, 35, 40), comprising a valve opening (15, 37, 47) through which a fluid can flow, arranged between a fluid inlet (9) and a fluid outlet (10), and a sealing body (12, 41), which is opened by means of a fluid flow is movable and covers the valve opening (15, 37, 47) in a closed position and releases it in an open position, the sealing body (12, 41) having an inflow side (16, 43) facing the valve opening (15, 37, 47) and one of the valve opening (15, 37, 47) has a groundbreaking outflow side (17, 44), the inflow side (16, 43) and the outflow side (17, 44) being delimited by a common radial edge (18, 31, 48), whereby the inflow side (16, 43) has a central sealing surface (19, 45), by means of which the valve opening (15, 37, 47) can be covered in the closed position, and in the open position of the sealing body (12, 41) its radial edge (18, 31, 48) can be flowed around by a fluid flow (L), characterized in that at least on the inflow side (16, 43) radially between the central sealing surface (19, 45) and the radial edge (18, 31, 48) of the sealing body (12, 41) a plurality of flow influencing elements (20a-20h, 21a-21h, 22a-22l, 23a-23p, 26a-26p, 27a-27p, 28a-28h, 29, 30a-30p, 32, 49) are arranged or designed. Valve after Claim 1 , characterized in that the flow influencing elements (20a-20h, 21a-21h, 22a-22l, 23a-23p, 26a-26p, 27a-27p, 28a-28h, 29, 30a-30p, 32, 49) are designed and arranged in this way are that by means of these a fluid flow (L) passing through the valve opening (15, 37, 47) and the sealing body (12, 41) is divided into a plurality of partial parts before leaving the radial edge (18) of the sealing body (12, 41). Fluid flows (T1, T2) can be divided. Valve after Claim 1 , characterized in that the flow influencing elements (20a-20h, 21a-21h, 22a-22l, 23a-23p, 26a-26p, 27a-27p, 28a-28h, 29, 30a-30p, 32, 49) are designed and arranged in this way are that by means of these small flow vortices can be generated in a targeted manner in a fluid flow (L) passing through the valve opening (15, 37, 47) and the sealing body (12, 41). Valve according to one of the Claims 1 until 3 , characterized in that the flow influencing elements (20a-20h, 21a-21h, 22a-22l, 23a-23p, 26a-26p, 27a-27p, 28a-28h, 29, 30a-30p, 32, 49) on the inflow side ( 16, 43) and additionally, the radial edge (18, 31, 48) of the sealing body (12, 41) are arranged or formed on the outflow side (17, 44). Valve according to one of the Claims 1 until 4 , characterized in that flow influencing elements (23a-23p, 26a-26p, 27a-27p, 28a-28h, 29, 30a-30p, 32, 49) on the inflow side (16, 43) of the sealing body (12, 41) and additionally are arranged or formed on the valve opening (15, 37, 47). Valve according to one of the Claims 1 until 5 , characterized in that the valve (11, 35) is a reed valve, the sealing body (12) of which is designed as an elastic, largely plate-shaped and / or circular or annular lamella. Valve after Claim 6 , characterized in that the sealing body (12) additionally has an elastic fastening arm (13) of the same material. Valve according to one of the Claims 1 until 5 , characterized in that the valve (40) is a check valve whose sealing body (41) has a bell-like geometry. Valve according to one of the Claims 1 until 8th , characterized in that at least some of the flow influencing elements (20a-20h, 21a-21h, 22a-22l) of the sealing body (12, 41) are designed as holes, the respective edge of which forms the inflow side (16, 43) and the outflow side (17, 44) connects to one another, with several of these hole-shaped flow influencing elements (20a-20h, 21a-21h, 22a-22l) being formed close to the radial edge (18, 31, 48) of the sealing body (12, 41) without reaching it. Valve after Claim 9 , characterized in that the hole-shaped flow influencing elements (20a-20h, 21a-21h, 22a-22l) have a circular, stadium-shaped or elliptical geometry. Valve after Claim 9 or 10 , characterized in that the hole-shaped flow influencing elements (21a-21h) have a polygonal or rectangular geometry, in particular with rounded corners. Valve after Claim 11 , characterized in that the hole-shaped flow influencing elements (21a-21h) have a ring segment-shaped geometry, in particular with rounded corners. Valve according to one of the Claims 9 until 12 , characterized in that the hole-shaped flow influencing elements (22a-22l) are notch-shaped incisions in the. arranged radially away from the central sealing surface (19, 45). Sealing body (12, 41) are formed without reaching its radial edge (18). Valve according to one of the Claims 1 until 8th , characterized in that at least some of the flow influencing elements (23a-23p, 26a-26p, 27a-27p) are designed as guide fins, which in the radial cross section have the geometry of a right-angled or similar triangle and in the plan view the geometry of a rectangle, a triangle or of a trapezium, wherein a first side (24) of the respective guide fin-shaped flow influencing elements (23a-23p, 26a-26p, 27a-27p) is flush with the radial edge of the sealing body (12, 41) and a second side (25) of the respective guide fin is flat resting on the inflow side (16, 43) and firmly connected to it, and wherein several of these guide fin-shaped flow influencing elements (23a-23p, 26a-26p, 27a-27p) are arranged along the radial edge (18, 31, 48) of the sealing body ( 12, 41) are arranged. Valve according to one of the Claims 1 until 8th , characterized in that at least some of the flow influencing elements (28a-28h) are designed as ring segment-shaped blocks which are formed on the inflow side (16, 43) or are firmly connected to it, with several of these block-shaped flow influencing elements (28a-28h) along the radial Edge (18, 31, 48) of the sealing body (12, 41) are arranged. Valve according to one of the Claims 1 until 8th , characterized in that at least some of the flow influencing elements (30a-30p) are designed as tunnels, and that these tunnel-shaped flow influencing elements (30a-30p) each have the cross-sectional geometry of a hollow profile. Valve after Claim 16 , characterized in that the tunnel-shaped flow influencing elements (30a-30p) each have the cross-sectional geometry of a semicircle, these tunnel-shaped flow influencing elements being arranged flat on the inflow side (16, 43) of the sealing body (12, 41) and being firmly connected to it, whereby the tunnel-shaped flow influencing elements (30a-30p) on the inflow side (16, 43) extend starting radially away from the central sealing surface (19, 45) up to the radial edge (18, 31, 48) of the sealing body (12, 41), and wherein several of these tunnel-shaped flow influencing elements (30a-30p) are arranged along the radial edge (18, 31, 48) of the sealing body (12, 41). Valve according to one of the Claims 1 until 6 , characterized in that at least some of the flow influencing elements (32) are designed as guide teeth, which are arranged or formed along the radial edge (31) of the sealing body (12), these tooth-shaped flow influencing elements (32) being at least partially connected to the inflow side (16). of the sealing body (12) form a plane. Valve according to one of the Claims 1 until 6 , characterized in that at least some of the flow influencing elements (32) are designed as guide teeth, which are arranged or formed along the radial edge (31) of the sealing body (12), these tooth-shaped flow influencing elements (32) being at least partially in the flow direction towards the outflow side ( 17, 44) of the sealing body (12) are curved. Valve according to one of the Claims 1 until 19 , characterized in that the flow influencing elements (20a-20h, 21a-21h, 22a-22l, 23a-23p, 26a-26p, 27a-27p, 28a-28h, 30a-30p, 32, 49) on the radial edge (18, 31, 48) of the sealing body are arranged or designed to be distributed equidistant from one another over its circumference. Valve according to one of the Claims 1 until 19 , characterized in that the flow influencing elements (20a-20h, 21a-21h, 22a-22l, 23a-23p, 26a-26p, 27a-27p, 28a-28h, 30a-30p, 32, 49) on the radial edge of the sealing body such are arranged or designed close to one another so that they form a circumferential, at least largely continuous flow influencing edge. Valve according to one of the Claims 1 until 21 , characterized in that a plurality of annular rows of flow influencing elements (49) are arranged or formed in the radial direction between the central sealing surface (19, 45) and the radial edge (18, 31, 48) of the sealing body (12, 41). Pneumatic compressor (1) with a valve (11, 35, 40) which has the features of at least one of Claims 1 until 22 having. Hydraulic pump with a valve (11, 35, 40) which has the features of at least one of the Claims 1 until 22 having.

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