DE102022113977A1 - Pneumatic valve and compressor - Google Patents

Abstract

The invention relates to a pneumatic valve (20, 30) for a compressor (1) with a valve opening (21, 31, 131, 231, 331) through which flow can flow and a valve body (22, 32, 132, 232, 332) which is located on the Valve opening (21, 31, 131, 231, 331) can be moved between an open position (18) and a closed position (19) and two cover surfaces (33, 34 133, 233, 333) and a body edge connecting both cover surfaces (33, 34). (35, 135, 235, 335). The first cover surface (33, 133, 233, 333) is designed to cover the valve opening (21, 31, 131, 231, 331) in the closed position (19), with a section of the body edge (35) in the open position (18). , 135, 235, 335) can be flowed around by an air flow (L). The invention proposes that the body edge (35, 135, 235, 335) in the area of the section (36, 136, 236, 336) around which the air flows has a number of shapes (37, 137, 237, 337) for scattering the air flow (L). along the body edge (35, 135, 235, 335).

Description

The invention relates to a pneumatic valve according to the preamble of claim 1, a compressor according to the preamble of claim 16, a vacuum pump according to the preamble of claim 17 and a vehicle according to claim 18. The invention relates in particular to pneumatic valves for a compressor, in particular a piston compressor .

Pneumatic valves of the above type include a valve opening arranged between an air supply connection and a compressed air outlet and through which flow can flow in a flow direction, and a valve body which can be moved pneumatically at the valve opening between an open position and a closed position. The valve body has a first cover surface, a spaced-apart second cover surface and a body edge connecting the first cover surface and the second cover surface. In such pneumatic valves, the first cover surface is designed to cover the valve opening in the closed position. In the open position, at least a section of the body edge can be flowed around by an air flow. Such valve bodies can usually be moved dynamically or highly dynamically to achieve short response times.

Pneumatic valves are used, for example, in vacuum pumps and compressors in vehicles. Such compressors or compressors are used, for example, to supply compressed air to a compressed air supply system. Compressors, especially piston compressors in all types of vehicles, are commonly known. They are used to provide compressed air and cover many areas of application, including brake systems, air suspension systems, especially for level control, clutch boosters and many more. Important target criteria when designing compressors include the highest possible delivery rate, the lowest possible noise development, the smallest possible dimensions, low manufacturing effort and high robustness.

Piston compressors usually include a valve seat plate that acts as a valve carrier and is arranged between a cylinder housing and a cylinder head of the piston compressor, as well as at least one suction valve and pressure valve attached to the valve seat plate. In addition to an inlet chamber and an outlet chamber, the cylinder head can preferably also have a relief chamber and a relief valve. Such relief valves are used to connect, if necessary, a working space formed in the cylinder housing to the relief chamber. The cylinder head of a piston compressor is usually made as a die-cast component from a light metal alloy and is usually screwed to the cylinder housing of the piston compressor via the valve seat plate, to which the suction and pressure valves, which are primarily designed as plate or reed valves, are attached. The inlet chamber is connected to the environment via a filter arrangement and is connected to the working space of the cylinder housing in the suction tract of the associated piston via usually several valve openings arranged in the valve seat plate through a then opened suction valve, for example designed as a plate or reed valve. In the pressure section of the associated piston, the working space of the cylinder housing is connected to the outlet chamber via at least one further valve opening arranged in the valve seat plate, in particular an outlet channel, through a then opened pressure valve, which is connected to a delivery line of the compressed air supply system.

The concept of a two-stage compressor has proven successful, in which the supplied air is first compressed to a low-pressure level in a low-pressure stage and then to a high-pressure level in a high-pressure stage connected to the low-pressure stage, with a pressure valve and a suction valve being assigned to both stages.

In pneumatic systems, such as piston compressors or pneumatic valves in general, dynamic pressure changes in a fluid lead to so-called pressure surges or pressure hammers. Such a dynamic pressure change in a pneumatic system occurs when a valve is opened or closed quickly. To open or close the valve, a fluid in the pneumatic system must be accelerated or decelerated, which requires a certain amount of force due to the inertia of the fluid. The necessary force results in a change in pressure and thus causes the pressure surge. Pressure surges could only be avoided with infinitely slow opening and closing processes. Due to the response times required in compressors, for example, pressure surges are unavoidable in real operation. The resulting pressure is passed on by pressure waves, which are longitudinal waves. Excessive pressure surges can cause damage to the affected pneumatic system. Furthermore, pressure surges lead to an excitation of the pneumatic system, which responds with a resonance oscillation with a natural frequency. The acceleration of the fluid also causes turbulent flows, which stimulate the oscillatory components of a valve that flow around and thus cause strong noise development. Such turbulences are particularly present in the edge area zen therefore undesirable. Particularly affected by such turbulence is the valve body, which is movably accommodated in such a valve and 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 valve body, it is particularly susceptible to being massively excited by the pressure surge and causing undesirable noise development.

This is where the invention comes in, the task of which is to reduce the noise generated when opening and closing a pneumatic valve of the type mentioned or to overcome at least one of the disadvantages known from the prior art.

The object is solved in a first aspect by a valve with the features of claim 1. The invention proposes that the body edge has a number of formations, at least in the area of the flow-around section, which are designed to close the air flow along the body edge scatter. The scattering of the air flow results in a diffuse distribution, so that streamlines run in different, sometimes opposite directions. The individual flow particles therefore move in sometimes opposite directions and collide with each other, whereby the kinetic energy of the accelerated flow is reduced. This reduces the excitation of surrounding components by the air flow. Furthermore, the sound generated by the diffuse flow on the valve body spreads in different directions, whereby the sound waves overlap and cancel each other out to a certain extent. This reduces the noise generated from the valve body.

It should be understood that the first cover surface and the second cover surface do not have to run parallel to one another. However, at least the first cover surface of the valve body is designed such that it completely covers the valve opening in the closed position and comes into contact with it in such a way that the air supply connection is separated from the compressed air outlet in a fluid-tight manner in the closed position. With the aim of reliably covering the valve opening through the cover surface, a narrow overlap area is usually provided, in which the first cover surface projects beyond or overlaps the cross section of the valve opening. The body edge does not have to run perpendicularly between the first cover surface and the second cover surface, but can also be inclined relative to them. Furthermore, the first cover surface and the second cover surface can merge radially into the body edge, that is to say in a circular arc section which extends between a flat section of the respective cover surface and the body edge.

The formations are preferably designed to divide the air flow along the body edge into partial flows, in particular in a division ratio that corresponds to the number of formations. By dividing the air flow into several partial flows, the streamlines of which differ, particularly in terms of their direction, there is a reduced excitation of the oscillatory components around which the air flows. Furthermore, vibration excitation occurs in a large number of different frequencies, which are assigned to the respective partial flows. These overlapping and sometimes counteracting excitations of the parts around which the flow flows lead overall to reduced excitation and thus noise development. In particular, the direction of the pressure surge, which is caused when the valve is opened or closed, becomes diffuse due to the large number of partial flows and is smaller in magnitude in relation to a defined area.

Preferably, the division ratio in which the air flow is divided into partial flows is 1/10 or less, particularly preferably 1/40 or less. With a division ratio of 1/10 or less, at least ten formations are provided, which divide the air flow into a total of at least ten partial flows. With a division ratio of 1/40, at least 40 formations are provided, which divide the air flow into at least 40 partial flows. The higher the number of partial flows, the lower the excitation caused by the respective partial flow.

Further preferably, the first cover surface has a base surface for covering the valve opening, with the formations extending distally from this base surface. The formations extending distally outwards from the base area ensure that the valve opening is reliably covered by the base area in the closed position. Such a valve body is produced in particular by etching to form the body edge, such that the base area is preferably retained and formations are formed along the base area or the body edge surrounding the base area, at least in the area of the body edge that will later be surrounded by flow.

It is further preferred that the formations extend distally from the base surface with a length L, the length L being 0.2 mm to 0.8 mm, preferably 0.4 mm to 0.6 mm. The formations therefore have sufficient length to divide the air flow into partial flows and allow the air to flow through between them individual formations to achieve a gradual pressure equalization between the pressure and suction side. At the same time, the dynamic movement of the valve body, which is particularly required in pneumatic valves for compressors, is not impaired by the additional weight and excessive length of the formations. More preferably, the formations on the base surface have a width of 0.3 mm to 1.5 mm, particularly preferably 0.4 mm to 1 mm.

The formations are preferably convex, with a free space being provided between two adjacent formations. This free space is set up to carry out a partial flow of the scattered or divided air flow. The free spaces defined between the convex formations, which form a kind of niche between the formations, provide a gradual pressure equalization between the pressure side and the suction side of the valve body. This pressure equalization reduces the noise generated when opening and closing the valve. The convex design of the formations also does not affect the closing function of the valve body, which is intended to cover the valve opening in the closed position.

Furthermore, it is preferred that the formations are arranged evenly distributed in the area of the flow-around section. The air flow is thus spread evenly through the formations along the section around which the air flows or is divided into individual partial flows.

The formations are preferably arranged at a distance of 0.2 mm to 0.5 mm, particularly preferably at a distance of 0.3 mm to 0.4 mm, from one another. A sufficient distance is therefore provided between the formations in order to provide pressure equalization between the pressure side and the suction side. Furthermore, the air flow is divided into sufficiently small partial flows by the spacing of 0.2 mm to 0.5 mm, so that the noise when opening and closing the valve is reduced.

Preferably, the formations extend continuously along the body edge in the area of the flow-around section. In other words, the formations extend continuously along the body edge in the area of the flow-around section in such a way that the air flow is scattered over the entire area of the flow-around section or is divided into individual air flows. It should be understood that this distribution of the formations leaves no section of the body edge of more than 1 mm in which no formations are arranged. By continuously extending the number of formations along the edge of the body, noise reduction is further optimized.

According to a preferred embodiment, the formations are uniform in a continuous section of the body edge. In the present case, a continuous section of the body edge is understood to mean either a straight, linear edge or a body edge extending along a circular path with a constant radius. Due to the uniform design of the formations in this continuous section, the air flow is evenly divided or scattered into partial flows, so that a large number of uniform partial flows are generated, the streamlines of which run in different directions. The noise generated by the pneumatic valve is thus further reduced by the large number of uniform and, in particular, fine partial flows.

The formations are preferably trapezoidal. In the present case, a trapezoidal shape is understood to mean a cross-sectional shape of an elongated, distally tapering trapezoid. On the side of the base surface, the formations therefore have a maximum cross section and taper in the distal direction. Thus, the air flow is not only suitably divided into partial flows, but is also deflected along the trapezoidal shapes in such a way that the turbulent flows are smoothed and scattered. The tip of the trapezoidal formations is preferably rounded, so that the pressure equalization between the pressure side and the suction side is improved.

According to a further preferred embodiment, the valve body is bent at least in sections in the flow direction adjacent to the body edge in the area of the flow-around section. In other words, the valve body is bent at the edge in the direction of flow in the area of the section of the body edge around which the flow flows. This bend in the direction of flow smooths out small turbulent vortices contained in the flow over the deck surface and gradually directs them towards the edge of the body, so that they produce less sound when interacting with the edge of the body. Furthermore, the valve body can also be bent in the direction of flow only in the area of the formations. Even a slight bend in the area of the formations leads to a smoothing of the flow and thus reduced noise development. It should be understood that the valve body is only bent to such an extent that the top surface or the base surface of the top surface can still sufficiently cover the valve opening in the closed position.

Preferably, the body edge has a height of 1 mm or less, in particular 0.5 mm or less. This height is constant when the top surfaces are aligned parallel. Otherwise, the second cover surface is arranged at a varying distance from the first cover surface, so that the height of the body edge also varies within this area.

The valve body is preferably set up for dynamic movement between the open position and the closed position. The small thickness of the valve body, defined by the distance between the first cover surface and the second cover surface, enables dynamic movement of the valve body between the open position and the closed position. A dynamic movement is advantageous in order to be able to achieve short response times of the pneumatic valve.

According to a preferred embodiment, the pneumatic valve is a plate valve and the valve body is a valve plate. Plate valves usually include a valve seat body, a catcher or lift catcher and at least one valve plate that can be moved back and forth between them. The valve openings are formed in the seat body, with the valve plate being movable back and forth between the open position, in which the valve openings are exposed, and the closed position. The seat body forms the valve seat on which the valve plate rests as a valve body. The valve openings preferably extend through both the seat body and the lift catcher, with the valve plate closing or covering the valve openings in the closed position, as described above. The valve plate can have a plurality of body edges, with at least a portion of the body edges being flowed around by the air flow. Each of these body edges preferably has a number of recesses, at least in the area of a section around which flow flows.

According to a further preferred embodiment, the pneumatic valve is a reed valve and the valve body is a valve reed. Lamella valves usually include a seat body or valve seat body and a stroke catcher, with the valve disk being arranged between the seat body and the stroke catcher. The valve lamella can be pneumatically actuated in such a way that, for example, it carries out a lifting movement from the closed position to the open position in order to selectively release the valve opening, with the stroke catcher limiting the lifting movement of the valve lamella. This prevents the valve lamella from opening too far and prevents damage, for example due to deformation of the valve lamella. Furthermore, short response times can be achieved by limiting the lifting movement. Valve bodies designed as valve lamellas usually have a very low weight and are dynamically movable. Due to their low weight, valve slats are very susceptible to vibrations caused by turbulent flows. With regard to lamellar valves with a valve body designed as a valve lamellar, formations along the body edge, at least in the area of the flow-around section of the body edge, are therefore particularly advantageous.

In a second aspect, the invention relates to a compressor, in particular a compressor of a compressed air system. Compressors according to the second aspect of the invention are used in particular for supplying compressed air to a compressed air supply system. Compressors according to the second aspect of the invention have a cylinder housing with at least one compression space, an air supply connection and a compressed air outlet. Furthermore, the compressor comprises a cylinder head connected to the cylinder housing, a piston guided in an axially movable manner with the cylinder housing, at least one valve seat plate which is arranged between the cylinder housing and the cylinder head, an inlet valve connected to the air supply connection and an outlet valve connected to the compressed air outlet. The inlet valve and the outlet valve are in particular attached to the valve seat plate, the valve seat plate forming a valve seat for the inlet valve and the outlet valve and having at least one valve opening. The inlet valve is preferably a suction valve and the outlet valve is a pressure valve. In order to solve the aforementioned problem according to the second aspect of the invention, the invention proposes that the suction valve and/or the pressure valve are designed according to the first aspect of the invention.

Compressed air systems are well known. They are used to subject air to a defined pressure and, for example, to create a negative pressure or to provide compressed air. A brake booster or a compressed air supply system represent examples of such compressed air systems. By designing the inlet valve and / or the outlet valve as a pneumatic valve according to the first aspect of the invention, the compressor adopts the advantages of the pneumatic valve according to the first aspect of the invention mentioned at the beginning. To avoid repetition, reference is made to the stated advantages and preferred embodiments of the pneumatic valve according to the first aspect, which are also preferred embodiments and advantages of the compressor according to the second aspect of the invention.

The inventors advantageously recognized that most of the noise is caused by the turbulence at the body edge of the free end of the valve body with flow around it. The body edge with the shapes smooths the air flow and the currents are dispersed. On the one hand, the air permeability between the individual projections leads to a gradual pressure equalization between the top (the so-called suction side) and the bottom (pressure side) of the valve body. As a result, the pressure difference at the actual rear edge of the valve body is less strong and less noise is generated. In addition, the flexibility of the edge area is also said to have an acoustic effect.

In a third aspect, the invention relates to a vacuum pump for generating a negative pressure, in particular for generating a negative pressure in a compressed air system, in particular a brake booster in a vehicle. The vacuum pump comprises a pump housing with an air supply connection and a compressed air outlet, and a rotor which is rotatably accommodated in the pump housing and is designed to convey and compress a fluid between the air supply connection and the compressed air outlet. Furthermore, the vacuum pump includes an inlet valve connected to the air supply port and an outlet valve connected to the compressed air outlet, the inlet valve and the outlet valve being attached to the valve seat plate.

In order to solve the aforementioned problem according to the third aspect of the invention, the invention proposes that the inlet valve and/or the outlet valve are designed according to the first aspect of the invention.

By designing the inlet valve and/or the outlet valve as a pneumatic valve according to the first aspect of the invention, the vacuum pump adopts the aforementioned advantages of the pneumatic valve according to the first aspect of the invention. To avoid repetition, reference is made to the stated advantages and preferred embodiments of the pneumatic valve according to the first aspect, which are also preferred embodiments and advantages of the vacuum pump according to the third aspect of the invention.

In a fourth aspect, the invention relates to a vehicle, in particular a commercial vehicle, with a compressor of a compressed air system according to the second aspect of the invention and / or a vacuum pump of a compressed air system according to the third aspect of the invention. Because the compressor and the vacuum pump have a pneumatic valve according to the first aspect of the invention, the vehicle also takes advantage of the aforementioned advantages of the pneumatic valve according to the first aspect of the invention. To avoid repetition, reference is made to the stated advantages and preferred embodiments of the pneumatic valve according to the first aspect, which are also preferred embodiments and advantages of the vehicle according to the fourth aspect of the invention.

Embodiments of the invention will now be described below with reference to the drawing. This is not necessarily intended to represent the embodiments to scale; rather, where useful for explanation, the drawing is carried out in a schematic and/or slightly distorted form. With regard to additions to the teachings immediately recognizable from the drawing, reference is made to the relevant state of the art. It should be noted that various modifications and changes can be made to the form and detail of an embodiment without departing from the general idea of the invention. The features of the invention disclosed in the description, in the drawing and in the claims can be essential for the development of the invention both individually and in any combination. In addition, all combinations of at least two of the features disclosed in the description, the drawing and/or the claims fall within the scope of the invention. The general idea of the invention is not limited to the exact form or detail of the preferred embodiments shown and described hereinafter or limited to a subject matter that would be limited in comparison to the subject matter claimed in the claims. For specified design ranges, values within the specified limits should also be disclosed as limit values and can be used and claimed as desired. For the sake of simplicity, the same reference numbers are used below for identical or similar parts or parts with identical or similar functions.

• 1: einen Verdichter mit einem pneumatischen Ventil schematisch;
• 2a: ein pneumatisches Ventil gemäß einer ersten Ausführungsform schematisch;
• 2b ein Ausschnitt des Ventilkörpers des pneumatischen Ventils gemäß 2a;
• 3: ein pneumatisches Ventil gemäß einer zweiten Ausführungsform schematisch;
• 4: einen Ventilkörper für das Ventil gemäß 2a gemäß einer ersten Ausführungsform;
• 5: einen Ventilkörper für das Ventil gemäß 3 gemäß einer zweiten Ausführungsform;
• 6: einen Ventilkörper für ein Ventil gemäß 3 gemäß einer dritten Ausführungsform;
• 7a eine Vakuumpumpe in einer perspektivischen Ansicht;
• 7b eine Vakuumpumpe in einer Seitenansicht; und
• 8 ein Fahrzeug mit einer Druckluftanlage in einer Seitenansicht.

Further advantages, features and details of the invention result from the following description of the preferred embodiments and from the drawings, which show in:

• 1 : a compressor with a pneumatic valve schematically;
• 2a : a pneumatic valve according to a first embodiment schematically;
• 2 B a section of the valve body of the pneumatic valve according to 2a ;
• 3 : a pneumatic valve according to a second embodiment schematically;
• 4 : a valve body for the valve according to 2a according to a first embodiment;
• 5 : a valve body for the valve according to 3 according to a second embodiment;
• 6 : a valve body for a valve according to 3 according to a third embodiment;
• 7a a vacuum pump in a perspective view;
• 7b a vacuum pump in a side view; and
• 8th a vehicle with a compressed air system in a side view.

The 1 shows a compressed air system 100 for a vehicle (not shown). In the embodiment shown, the compressed air system is a compressed air supply system 110. The compressed air supply system 110 comprises a compressor 1 and a compressed air storage 12, which is connected to the compressor 1 via a compressed air line 15. Further elements of the compressed air system 100 can be connected to the compressed air line 15, such as an air dryer and a multi-circuit protection valve in brake systems in commercial vehicles. Such known elements of compressed air systems 100 are in the 1 Not shown for simplicity and are symbolized by the compressed air line 15.

The compressor 1 is designed as a piston compressor 7 or piston compressor 8. It 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. As shown 1 The compression space 4 is arranged above the piston 3, the neutral space 5 is arranged below the piston 3. For pneumatic separation of the compression space from the neutral space, the piston 3 has a circumferential seal. On the side of the piston 3 facing away from the compression space 4, there is a crankcase 10 of the compressor 1 next to the neutral space 5. The interior of the crankcase 10 is connected to the neutral space 5, that is, the neutral space 5 is at the pressure level of the interior of the crankcase 10. The neutral space 5 can also be part of the interior of the crankcase 10.

The piston 3 is, as is known in piston compressors, connected via a connecting rod 11 to a drive shaft (not shown) designed as a crankshaft.

By rotating the drive shaft (not shown), the piston 3 is moved upwards or downwards by means of the connecting rod 11. A downward movement corresponds to a suction phase of the compressor 1, in which the compression space 4 is enlarged. During the suction phase, as a result of a negative pressure created in the compression space 4, an inlet valve 20 designed as a suction valve opens for a compressed air supply 9. As a result, ambient air flows into the compression space 4 via an air supply connection 13 of the compressor 1 that is connected to the atmosphere. When the piston 3 moves upwards, 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 compressed, which leads to an increase in pressure in the compression space 4. This closes the inlet valve 20. The pressure in the compression chamber 4 continues to increase until either an outlet valve 30 designed as a pressure valve opens or the piston 3 reaches its top dead center. The outlet valve 30 opens when the pressure in the compression chamber 4 exceeds the pressure in the area of a compressed air outlet 14 of the compressor 1. The compressed air outlet 14 of the compressor 1 is connected to the other elements of the compressed air system 100, in particular to the compressed air reservoir 12, via the compressed air line 15 mentioned.

A valve seat plate 16 is mounted between the cylinder housing 2 and the cylinder head 6. The inlet valve 20 and the outlet valve 30 are attached to the valve seat plate 16 and in the present case are designed as a reed valve 41.

The inlet valve 20 includes a valve opening 21, which is arranged between the air supply connection 13 and the compressed air outlet 14 and can flow through in a flow direction Rs. Furthermore, the inlet valve 20 comprises a valve body 22, which can be moved pneumatically actuated between an open position 18 and a closed position 19 at the valve opening 21. The valve body 22 of the inlet valve 20 is shown in the open position 18 here.

Corresponding to the inlet valve 20, the outlet valve 30 also includes a valve opening 31 between the air supply connection 13 and the compressed air outlet 14, through which flow can flow in the flow direction Rs. Furthermore, the outlet valve 30 also includes a valve body 32, which is pneumatically actuable and movable between the open position 18 and the closed position 19 at the valve opening 31. The valve body 32 of the outlet valve 30 is shown in the closed position 19 here.

2a shows a first embodiment of an exhaust valve 30 schematically. In a corresponding way, the in 1 Inlet valve 20 shown can be formed, so that reference is made to the following statements with regard to the inlet valve 20. In principle it can be the case in 2a The valve shown is any pneumatic valve, for example for compressors or vacuum pumps.

The exhaust valve 30 includes, as related to 1 described, the valve body 32 and the valve opening 31, which are selectively in the closed position 19 (cf. 1 ) is closed by the valve body 32. The valve opening 31 is in the open position 18 (cf. 1 ) can flow through in a flow direction R _s .

The valve body 32 includes a first cover surface 33 and a spaced apart second cover surface 34. The first cover surface 33 and the second cover surface 34 are connected by a body edge 35. The first cover surface 33 is designed to keep the valve opening 31 in the closed position 19 (cf. 1 ) to cover. In 2a the outlet valve 30 is in the open position 18 (cf. 1 ) shown, in which at least a section 36 of the body edge 35 is flowed around by an air flow L.

The body edge 35 has a number of formations 37 in the area of the flow-around section 36. The formations 37 are designed to scatter the air flow L along the body edge 35, with the air flow L being smoothed in particular in the area of the body edge 35.

The first cover surface 34 has a base surface 38 through which the valve opening 31 is in the closed position 19 (cf. 1 ) is covered. The formations 37 extend distally outwards from the base surface 38 with a length x. The formations 37 are arranged at a distance from one another and are preferably designed to divide the air flow L into partial flows L1, L2.

The body edge 35 has a height h, which is constant in the present case.

2 B shows a detailed representation of the valve body 32 according to 2a . The air flow L is divided along the body edge 35 into partial flows L1, L2. The air flow L is divided in a division ratio T, which corresponds to the ratio of one air flow L to the number of partial flows L1, L2. This division ratio T is preferably proportional to the number of formations 37, since two adjacent formations are arranged at a distance A from one another and each form a free space 45 between them. A partial flow L1, L2 is then conducted through this free space 45.

The formations 37 extend with a length X from the base area 38 and preferably have a width B on the side of the base area 38. 3 shows a second embodiment of the outlet valve 30, which is designed as a plate valve 42. For the same or similar components, 2 and 3 Identical reference numbers are used here. The embodiment shown is not limited to exhaust valves 30, but relates to pneumatic valves in general. For example, the inlet valve 20 can also be designed accordingly, so that reference is made to the following description with regard to the inlet valve.

The outlet valve 30 according to 3 differs from the exhaust valve according to 2a only through the design of the valve body 32. To avoid repetition, the detailed description of the valve 30 is therefore referred to 2a Referenced.

The valve body 32 according to 3 comprises, in a known manner, a first cover surface 33, which is used to cover the valve opening 31 in the closed position 19 (cf. 1 ) is set up. The valve body 32 further comprises a second cover surface 34, which is arranged at a distance from the first cover surface 33. The first cover surface 33 and the second cover surface 34 are connected by a body edge 35. The body edge 35 has a number of formations 37 in an area 36 around which the air flow L flows. The formations 37 are arranged at a distance from one another and are preferably designed to divide the air flow L into partial flows L1, L2

In an area 39 adjacent to the body edge 35, the valve body 32 is bent in the flow direction Rs. The formations 37 are preferably also arranged in this area 39. Through this curved area 39 adjacent to the body edge 35, the air flow L is further smoothed and the noise generated when opening and closing the outlet valve 30 is reduced.

The 4 until 6 show preferred embodiments of the valve body. The embodiments of the valve body shown are not limited to use in inlet valves or outlet valves, but can generally be used in pneumatic valves to close a valve opening. The one in the 4 until 6 For the sake of simplicity, the valve body shown is described below in relation to the exhaust valve 30.

The in 4 Valve body 132 shown is shown in a top view of a first cover surface 133. In the present case, the valve body 132 is a valve lamella 150 and also has a second top surface, not shown in the view. The first cover surface 133 and the second cover surface are connected to one another by a body edge 135.

The valve body 132 includes a flow-around section 136 and a mounting section 140.

The mounting section 140 has a number of bores 142, with only one of the bores being provided with a reference number for reasons of clarity. The mounting section 140 is firmly connected to the valve seat plate 16 via the bores 142 (cf. 1 ) tied together. This means that only the section 136 around which the air flows is affected by the air flow L (cf. 2a and 3 ) stimulated to oscillate.

The valve body 132 has two legs 143, 144 in the area of the flow-around section 136, with the body edge 135 extending along both legs 143, 144. Each of the legs 143, 144 is designed to cover a valve opening 31 (cf. 1-3 ) in the closed position 19 (cf. 1 ) furnished.

According to the 2 and 3 In the exemplary embodiment shown, the valve body 132 has a base area 138.1 on the first leg 143 and a second base area 138.2 on the second leg 144.

The mounting section 140 is connected to the legs 143, 144 through a transition region 147.

The first base area 138.1 is designed to have a first valve opening (not shown) in the closed position 19 (cf. 1 ) and the second base area 138.2 is designed to be in the closed position 19 (cf. 1 ) to cover a second valve opening (not shown). A number of formations 137 extend distally from the base surfaces 138.1, 138.2, with only one formation being provided with a reference number for reasons of clarity.

The formations 137 are evenly distributed in the area of the flow-around section 136. The formations 137 are preferably convex, so that a free space or a niche 145 is formed between two adjacent formations 137, which is used to carry out a partial flow L1, L2 of the scattered or . divided air flow L (cf. 2a and 3 ) is set up. The formations 137 extend continuously along the entire body edge 135 in the area of the flow-around section 136.

The body edge 135 has a number of continuous sections 146. The formations 137 are uniform in these continuous sections 146. For reasons of clarity, only one of the continuous sections 146 is provided with a reference number.

In the present case, it should be understood that continuous sections 146 denote both linear sections of the body edge 135 and sections of the body edge 135 extending along a circular arc section with a constant radius. In the present case, the body edge 135 is discontinuous in a transition region between the linearly extending section and that along a Circular arc section extending section of the body edge 135 on the two legs 143, 144. Only in this area are the formations 137 not uniform. The formations 137 are evenly spaced along the continuous sections 146.

The formations 137 are trapezoidal in cross section and have a distal curve 148. In addition to a rounded distal end, the formations 137 can also be flattened. Thus the air flow L (cf. 2a and 3 ) scattered by the number of formations 137. Due to the spacing of the formations 137, the air flow L (cf. 2a and 3 ) further into a number of partial flows L1, L2 corresponding to the number of formations 137 (cf. 2a and 3 ) divided up. The individual partial flows L1, L2 (cf. 2a and 3 ) ensure a reduced amount of excitation of the valve body 132 and thus a reduced noise development.

5 shows a second embodiment of a valve body 232 according to the invention. The valve body 232 shown is a valve plate 250 and for use in a plate valve 42 (cf. 3 ) furnished.

The valve body 232 in 5 points according to the previous in 4 Embodiment shown has a mounting part 240, wherein the flow around section 236 extends radially outside of the mounting part 240 around it. The valve body 232 has a substantially circular cross-sectional area. The flow around section 236 is designed in sections as a ring and is connected to the mounting part 240 in a transition area 247. The part 236 of the body edge 235 that flows around adjoins the transition section 247. The body edge 235 has continuous formations along the section 236 around which the flow flows 237, whereby for reasons of clarity only one of the formations 237 is provided with a reference number.

According to the previous in 4 The embodiment shown also extends into 5 the formations 237 distally from a base surface 238 of the valve body 232. The formations 237 are formed at regular intervals from one another and in particular are formed uniformly along the body edge 235. Thus the air flow L (cf. 2a and 3 ) into a number of partial flows L1, L2 corresponding to the number of formations 237 (cf. 2a and 3 ) divided up.

6 shows a third embodiment of a valve body 332 according to the invention for a pneumatic valve (cf. 2a and 3 ). The valve body 232 shown is a valve plate 350 and for use in a plate valve 42 (cf. 3 ) furnished.

The valve body 332 in 6 points according to the previous in 5 Embodiment shown has a mounting part 340 with a number of holes or partial holes 342. For reasons of clarity, only one of the partial bores 342 is provided with a reference number. The valve body 332 extends in sections along a circular path and forms a ring section with an interruption. The flow around section 336 is designed in sections as a ring and forms a first end of the annular valve body 332. A second end is formed by the mounting section 340.

The body edge 335 has formations 337 continuously along the flow-around section 336, with only one of the formations 337 being provided with a reference number for reasons of clarity.

According to the previous in 5 The embodiment shown also extends into 6 the formations 337 distally from a base surface 338 of the valve body 332. The formations 337 are formed at regular intervals from one another and in particular are formed uniformly along the body edge 335. Thus the air flow L (cf. 2a and 3 ) into a number of partial flows L1, L2 corresponding to the number of formations 337 (cf. 2a and 3 ) divided up.

In 7a and 7b a vacuum pump 400 is shown. The vacuum pump 400 has a housing 463, which is connected to a cover plate 463 by means of a number of screws 462. The pump housing 461 has a number of hexagon screws 464 for further assembly of the vacuum pump 400.

Furthermore, the pump housing 461 has an air supply port 413 for supplying air into a working chamber (not shown) of the vacuum pump 400. An inlet valve 420, not shown, is connected to the air supply connection 413, the position of which is only indicated.

The vacuum pump 400 is designed here as a rotary vane pump. A rotor 466 is rotatably accommodated in the pump housing 461, in particular the working chamber (not shown). The rotor 466 has rotary vanes (not shown) for conveying and compressing a fluid in the work space (not shown). A clutch 467 is connected to the rotor 466. The clutch 467 is designed to connect the rotor 466 to drive elements (not shown), for example a crankshaft.

Furthermore, the vacuum pump 400, as in particular in 7b shown, a compressed air outlet 414, which is selectively closed or released by a pneumatic valve, which in the present case is an outlet valve 430. The outlet valve 430 is designed as a reed valve 441, which is set up to vent the vacuum pump 400. The reed valve 441 includes a valve seat plate 416 with a valve opening (not shown). To selectively close the valve opening (not shown), the reed valve 441 has at least one valve reed 450. To limit the opening stroke of the valve disk 450, the disk valve 441 further comprises a stroke catcher 468. The valve disk 450 is according to one of the in the 2a until 4 embodiments shown.

Furthermore, the vacuum pump 400 can also have a pneumatic valve according to 2a until 4 at the air supply connection 413.

Of course, such a vacuum pump 400 can also have a plate valve instead of a reed valve 441.

8th shows a vehicle 1000, which in this case is a commercial vehicle 1001. The vehicle 1000 includes a compressed air system 100. This includes a compressed air supply system 110, which provides a compressed air supply for an air suspension system (not shown) and preferably a compressor 1 (not shown) according to 1 having. Furthermore, the compressed air system 100 includes a brake booster 120 (not shown). 7a and 7b .

Reference symbols

1

compressor

2

Cylinder housing

3

Pistons

4

Compression space

5

Neutral space

6

cylinder head

7

Piston compressor

8th

Piston compressor, compressor

9

Compressed air supply

10

crankcase

11

connecting rod

12

Compressed air storage

13, 414

Air supply connection

14,413

compressed air outlet

15

Compressed air line

16, 416

Valve seat plate

18

Open position

19

Closed position

20, 420

Pneumatic valve, inlet valve

21

Valve opening of the intake valve

22

Inlet valve body

30, 430

Pneumatic valve, exhaust valve

31

Valve opening of the exhaust valve

32, 132, 232, 332

Valve body of the exhaust valve

33, 133, 233, 333

first cover surface

34, 234, 334

second cover surface

35, 135, 235, 335

body edge

36, 136, 236, 336

flowed section

37, 137, 237, 337

Formations

38, 138, 238, 338

Floor space

39

curved section

41, 441

Lamella valve

100

Compressed air system

110

Compressed air supply system

120

Brake booster

140, 240, 340

Assembly part

142,242,342

drilling

143

first leg

144

second leg

145, 245, 345

free space

146

continuous section

147, 247

crossing

148

distal rounding

150, 450

valve lamella

250, 350

Valve plate

400

vacuum pump

461

Pump housing

462

screws

463

Cover plate

464

Hex screws

466

rotor

467

coupling

468

Lift catcher

1000

vehicle

1001

Commercial vehicle

L

Airflow

L1, L2

Partial flow

Rs

Direction of flow

X

Length of the shapes

b

Width of the shapes

H

Height of the edge of the body

A

Distance between the formations

T

Division ratio

Claims (18)

Pneumatic valve (20, 30, 420, 430) for a compressor (1), in particular a compressor (8), in particular for a compressed air supply (9) of a compressed air supply system (100), with a connection between an air supply connection (13) and a compressed air outlet ( 14) arranged and through which flow can flow in a flow direction (Rs) valve opening (21, 31, 131, 231, 331) and a valve body (22, 32, 132, 232, 332) which is attached to the valve opening (21, 31, 131, 231 , 331) pneumatic can be actuated and can be moved between an open position (18) and a closed position (19), the valve body (22, 32, 132, 232, 332) having a first cover surface (33, 133, 233, 333), a second cover surface (34) which is in contact with it. , and has a body edge (35, 135, 235, 335) connecting the first cover surface (33, 133, 233, 333) and the second cover surface (34), the first cover surface (33, 133, 233, 333) being designed for this purpose is to cover the valve opening (21, 31, 131, 231, 331) in the closed position (19), and in the open position (18) at least a portion of the body edge (35, 135, 235, 335) from an air flow (L) can be flowed around, characterized in that the body edge (35, 135, 235, 335) has a number of formations (37, 137, 237, 337), at least in the area of the flow-around section (36, 136, 236, 336), which are set up to scatter the air flow (L) along the body edge (35, 135, 235, 335). Pneumatic valve (20, 30, 420, 430). Claim 1 , characterized in that the formations (37, 137, 237, 337) are designed to divide the air flow (L) along the body edge (35, 135, 235, 335) into partial flows (L1, L2), in particular in one to divide the division ratio (T) corresponding to the number of formations (37, 137, 237, 337). Pneumatic valve (20, 30, 420, 430). Claim 2 , characterized in that the division ratio (T), in which the air flow (L) is divided into partial flows (L1, L2), is 1/10 or less, preferably 1/40 or less. Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the first cover surface (33, 133, 233, 333) has a base surface (38, 138, 238, 338) for covering the valve opening (21 , 31, 131, 231, 331) and the formations (37, 137, 237, 337) extend distally from this base surface (38, 138, 238, 338). Pneumatic valve (20, 30, 420, 430). Claim 4 , characterized in that the formations (37, 137, 237, 337) extend distally from the base surface (38, 138, 238, 338) with a length (X), the length being 0.2 mm to 0.8 mm b, preferably from 0.4 mm to 0.6 mm, the formations (37, 137, 237, 337) preferably having a width (B) on the base surface, which is in a range from 0.3 mm to 1 .5 mm, preferably from 0.4 mm to 1 mm. Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the formations (37, 137, 237, 337) are convex and between two adjacent formations (37, 137, 237, 337) respectively a free space (45, 145, 245, 345) is provided, which is set up to carry out a partial flow (L1, L2) of the scattered or divided air flow (L). Pneumatic valve (20, 30) according to one of the preceding claims, characterized in that the formations (37, 137, 237, 337) are evenly distributed in the area of the flow-around section (36, 136, 236, 336) of the pneumatic valve (20, 30) are arranged. Pneumatic valve (20, 30, 420, 430). Claim 7 , characterized in that the formations (37, 137, 237, 337) are arranged spaced apart from one another at a distance (A) of 0.2 mm to 0.5 mm, preferably 0.3 mm to 0.4 mm. Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the formations (37, 137, 237, 337) move continuously along the body edge (35, 135, 235, 335) in the area of the flow Section (36, 136, 236, 336). Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the formations (37, 137, 237, 337) are conical, in particular the trapezoidal formations (37, 137, 237, 337) a distal rounding (148). Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the formations (37, 137, 237, 337) are uniform in a continuous section of the body edge (35, 135, 235, 335). . Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the valve body (22, 32, 132, 232, 332) is adjacent to the body edge (35, 135, 235, 335) in the area of Flow around section (36, 136, 236, 336) is bent at least in sections in the flow direction (Rs). Pneumatic valve (20, 30) according to one of the preceding claims, characterized in that the body edge (35, 135, 235, 335) has a height (h) of 1 mm or less, in particular 0.5 mm or less, and the valve body (22, 32, 132, 232, 332) to a dynamic movement is set up between the open position (18) and the closed position (19). Pneumatic valve (20, 30) according to one of the preceding claims, characterized in that the pneumatic valve (20, 30) is a plate valve (42) and the valve body (232, 332) is a valve plate (250, 350). Pneumatic valve (20, 30, 420, 430) according to one of the preceding claims, characterized in that the pneumatic valve (20, 30) is a reed valve (41, 441) and the valve body (132) is a valve reed (150). Compressor (1), in particular a compressor (8), in particular for a compressed air supply (9) of a compressed air system (100), in particular a compressed air supply system (110), comprising: a cylinder housing (2) with at least one compression chamber (4), an air supply connection ( 13) and a compressed air outlet (14), a cylinder head (6) connected to the cylinder housing (2), a piston (3) guided axially movably in the cylinder housing (2), at least one valve seat plate (6) which is located between the cylinder housing (2 ) and the cylinder head (6), an inlet valve (20) connected to the air supply connection (13), and an outlet valve (30) connected to the compressed air outlet (14), the inlet valve (20) and the outlet valve (30). the valve seat plate (16), characterized in that the inlet valve (20) and / or the outlet valve (30) are designed according to one of the preceding claims. Vacuum pump (400) for generating a negative pressure for a compressed air system (100), in particular a brake booster (120) in a vehicle (1000), comprising: - a pump housing (461) with an air supply connection (413) and a compressed air outlet (414), and - a rotor (466) rotatably accommodated in the pump housing (461), which is set up to convey and compress a fluid between the air supply connection (413) and the compressed air outlet (414), an inlet valve (420) connected to the air supply connection (13), and a outlet valve (430) connected to the compressed air outlet (14), the inlet valve (420) and the outlet valve (430) being attached to the valve seat plate (16), characterized in that the inlet valve (420) and/or the outlet valve (430) are designed according to one of the preceding claims. Vehicle (1000), in particular commercial vehicle (1001), with a compressor (1). Claim 16 and/or a vacuum pump (400). Claim 17 for a compressed air system (100).

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