Cam-controlled distributor valve

Abstract

The invention relates to an outlet valve (1) comprising - an outlet opening (12) with a sealing edge (13), - a valve element (11) corresponding to the sealing edge, and - a carrier element (14) configured to lift the valve element off the sealing edge and to place it on the sealing edge preferably with play. The invention further relates to a distributor valve (2) and a distributor valve group (3).

Description

[0001] CAM-CONTROLLED DISTRIBUTION VALVE

[0002] AREA OF INVENTION

[0003] The present invention relates to an outlet valve, a distributor valve and a distributor valve group, particularly for industrial purposes.

[0004] BACKGROUND OF THE INVENTION

[0005] Distributor valves, which distribute a hydraulic or pneumatic fluid flow from one inlet to multiple outlets, are typically designed as spool or rotary spool valves. In these valves, the movement of a spool opens and closes various flow paths or outlets, for example, periodically. In high-pressure applications in oil hydraulics, the metallic seal is achieved through high-precision components. In low-pressure applications, such as water or gas applications, elastomer elements are used as an additional seal.

[0006] This presents the problem that the sliding of the slide in the intended direction of movement causes mechanical wear at the outlets and seals, and these are also subjected to uneven stress, or, depending on the design, the opening of the slide may be pulled over the sealing element. Furthermore, feeding two outlets simultaneously is usually only possible with two adjacent outlets.

[0007] SUMMARY OF THE INVENTION

[0008] The object of the invention is to provide an exhaust valve that operates with low wear, as well as a distributor valve and a distributor valve group that are flexibly switchable. This object is achieved by the subject matter of the independent claims. Preferred embodiments and further developments are specified in the dependent claims.

[0009] The outlet valve according to the invention comprises

[0010] - an outlet opening with a sealing edge,

[0011] - a valve element corresponding to the sealing edge of the outlet opening for opening and closing the outlet opening or the outlet valve, and - a guide or support element for the valve element, which is designed to lift the valve element from the sealing edge and place it on the sealing edge, preferably with clearance.

[0012] The (exactly one) outlet opening is a through-opening or continuous recess in a base body, for example, in a flat or horizontal base plate. The valve element-side edge of the outlet opening, which is also referred to below as the upper edge, is designed as a circular, circumferential, and / or flat, preferably rotationally symmetrical sealing edge against which the valve element engages (circumferentially). The sealing edge is designed to, or allows, the movable valve element or seat valve element to seal the outlet opening or to close and open the outlet valve. The sealing edge runs concentrically to a (vertical) axis of symmetry, which forms a valve axis of the outlet valve and may also simultaneously form a surface normal of the base body or base plate. The outlet opening is preferably a circular, rotationally symmetrical, cylindrical, and / or perpendicular shape to the valve axis.vertical recess, which preferably has a constant cross-section or diameter along the valve axis within the base body or base plate.

[0013] The exhaust valve according to the invention is configured to allow a hydraulic or pneumatic fluid to flow from a high-pressure side or pressurized side of the exhaust valve through the sealing edge or the exhaust opening to a low-pressure side of the exhaust valve. The high-pressure side of the exhaust valve is preferably formed by the valve element side of the sealing edge of the exhaust opening, that is, by the valve element-side portion of the exhaust valve relative to the sealing edge of the exhaust opening. The low-pressure side of the exhaust valve is preferably formed by the side of the sealing edge facing away from the valve element, that is, by the portion of the exhaust valve facing away from the valve element relative to the sealing edge of the exhaust opening, or by the inside of the exhaust opening. Accordingly, in this preferred embodiment, the valve element and the support element are (completely) arranged on the high-pressure side of the exhaust valve.

[0014] The pressure difference between the high-pressure and low-pressure sides of the outlet valve can be equal to the absolute pressure on the high-pressure side or be more than one, two, or three orders of magnitude lower. For example, the pressure difference is in the range of 1 to 10 mbar. The valve element is actuated from the high-pressure side, preferably entirely from the high-pressure side, so that, for example, no actuating element for the valve element is provided in the outlet opening. This minimizes the flow resistance and thus the pressure drop in the outlet opening during fluid flow, since, for example, no components such as plungers need to be provided within the outlet opening or on the low-pressure side of the outlet valve to actuate the valve element.During operation of the outlet valve, the pressure difference between the high-pressure side and the low-pressure side advantageously forces the valve element onto the sealing edge.

[0015] In the simplest case, the sealing edge is designed as a circumferential, rotationally symmetrical sealing edge with a right angle (90°) in the radial direction between (an inner wall) of the outlet opening and the valve element-side surface of the base body or base plate. The outlet opening is accordingly cylindrical, at least at its valve element-side upper edge, and preferably completely cylindrical. The sealing edge corresponds to the valve element for closing the outlet valve or sealing the outlet opening and / or, when the outlet valve is closed, is in continuous circumferential engagement with the valve element.

[0016] In an alternative embodiment, the sealing edge is designed as a circumferential, rotationally symmetrical sealing seat with a sealing seat surface inclined relative to the valve axis and / or extending over a surface area for the (continuous circumferential) engagement of the valve element. This annular and rotationally symmetrical seating surface thus extends not only in the direction of rotation but also perpendicular to the direction of rotation and / or has (at every point) a surface normal that intersects the valve axis and / or forms an angle with the valve axis other than zero and 90°. The seating surface of the sealing seat corresponds to the valve element for closing the exhaust valve or sealing the exhaust opening and / or is in continuous circumferential engagement with the valve element when the exhaust valve is closed.

[0017] In the simplest case, the seating surface of the sealing seat is conical or cone-shaped (as an internal cone) and / or has a surface normal at each point that includes a predetermined and / or constant angle of intersection with the valve axis, which is preferably in the range between 10° and 60°, particularly preferably between 20° and 40° and is, for example, 10°, 20°, 30°, 40°, 50° or 60°, wherein each of the mentioned values ​​can also represent an upper or lower limit of the mentioned value ranges.

[0018] In a preferred embodiment, the seat surface is (completely) spherical, that is, designed as a spherical surface or spherical segment. Preferably, the spherical surface of the sealing seat has exactly one predetermined and / or constant curvature or exactly one predetermined and / or constant radius of curvature, which is hereinafter also referred to as the sealing seat radius of curvature. The spherical center of the spherical segment of the sealing seat lies on the valve axis and is axially spaced from the sealing edge or is located on the valve element side relative to the sealing edge or the base body. All surface normals of the seat intersect at the spherical center.

[0019] The surface normals of the seat form different angles of intersection with the valve axis (corresponding to the curvature of the seat surface), varying within an angular range that is preferably between 2° and 15°, and particularly preferably between 8° and 12°, around a central angle, and which is, for example, 2°, 5°, 10°, or 15°, where each of the aforementioned values ​​can also represent an upper or lower limit of the aforementioned ranges. The central angle is preferably in the range between 10° and 60°, and particularly preferably between 20° and 40°, and is, for example, 10°, 20°, 30°, 40°, 50°, or 60°, where each of the aforementioned values ​​can also represent an upper or lower limit of the aforementioned ranges.The radius of curvature of the seating surface of the sealing seat is larger than the radius of the sealing edge, preferably by a factor in the range between 1.15 and 6, particularly preferably between 1.5 and 3, and is for example 1.15, 1.5, 2, 2.5, 3, 4, 5 or 6, wherein each of the mentioned values ​​can also represent an upper or lower limit of the mentioned value ranges.

[0020] The spherical seating surface of the sealing seat is preferably created by pressing an embossing ball or a corresponding and / or annular and spherical portion of an embossing element into the base body. The embossing ball or the spherical portion of the embossing element has the predetermined radius of curvature of the sealing seat (seal seat radius of curvature).

[0021] In a preferred embodiment, the preferably one-piece valve element is spherical, i.e., formed as a spherical surface, at least or exactly in an annular region corresponding to the sealing edge, that is, a concentric region circumferentially surrounding the valve axis. Accordingly, the valve element has a spherical surface or a spherical segment in this area and / or is completely rotationally symmetrical there. In the simplest case, the valve element is formed as a sphere, which is also referred to below as a spherical valve element. Alternatively, the valve element is formed as a hemisphere or hemispherical shell.

[0022] The spherical surface or spherical surface segment of the valve element has exactly one predetermined and / or constant curvature or radius of curvature, which is hereinafter also referred to as the valve element radius of curvature. Accordingly, all surface normals of the spherical surface or spherical surface segment of the valve element intersect at exactly one point, which is hereinafter also referred to as the spherical center of the valve element.

[0023] The radius of curvature of the valve element, or the radius of the sphere of the valve element designed as a sphere, is larger than the radius of the sealing edge, preferably by a factor in the range between 1.15 and 6, particularly preferably between 1.5 and 3, and is for example 1.15, 1.5, 2, 2.5, 3, 4, 5 or 6, wherein each of the mentioned values ​​can also represent an upper or lower limit of the mentioned value ranges.

[0024] If the sealing edge is designed as a spherical sealing seat, the radius of curvature of the valve element and the radius of curvature of the sealing seat are, in the simplest case, the same.

[0025] In a preferred embodiment, however, the sealing seat radius of curvature is larger than the valve element radius of curvature, preferably in the range between 1% and 20%, particularly preferably between 5% and 15% larger, for example by 1%, 2%, 3%, 5%, 8%, 10%, 12%, 15% or 20%, where each of the aforementioned values ​​can also represent an upper or lower limit of the aforementioned value ranges. Preferably, the spherical annular region corresponding to the sealing seat (perpendicular to the direction of rotation around the valve axis) in the valve element is wider than the sealing seat.

[0026] In a preferred embodiment, the valve element, in particular the ball valve element, consists entirely (homogeneously) or partially (e.g., as a coating or filler) of a plastic and / or elastomer, for example, EPDM (ethylene propylene diene monomer rubber), HNBR (hydrogenated nitrile butadiene rubber), FKM (fluorocarbon rubber), silicone, PP (polyphenylene), PE (polyethylene), PA (polyamide), PBT (polybutylene terephthalate), or PPS (polyphenylene sulfide). Such a valve element is preferably used for pneumatic and hydraulic fluids, especially aqueous fluids, at maximum or working pressures up to 20 bar, for example, at working pressures of 2, 4, 6, 8, 10, 12, 15, or 20 bar.

[0027] In a further preferred embodiment, the valve element, in particular the ball valve element, consists entirely or partially of a metal or a metal alloy, for example, stainless steel, brass, or aluminum. Such a valve element is preferably used for hydraulic fluids, in particular hydraulic oils, at maximum or operating pressures up to 200 bar, for example, at an operating pressure of 20, 40, 60, 80, 100, 120, 150, or 200 bar.

[0028] In the exhaust valve according to the invention, the movable guide or support element for the valve element is configured to lift the valve element from the sealing edge, particularly against the pressure forces acting between the high-pressure side and the low-pressure side. The lifting of the valve element from the sealing edge according to the invention is characterized in that the valve element is moved away from the sealing edge or lifted out of the sealing edge by the support element at a predetermined lifting angle relative to the valve axis, for example, exactly or substantially along the valve axis. Preferably, the lifting angle is smaller than the largest, and particularly preferably smaller than the smallest, angle of intersection of the surface normal of the sealing seat or the sealing edge designed as a sealing seat with the valve axis. Preferably, the lifting angle is smaller than or exactly 20°, 15°, 10°, 5°, 2°, 1°, or 0° relative to the valve axis.This lifting action prevents the valve element from sliding on the sealing edge and / or avoids one-sided stress on the sealing edge when the exhaust valve opens. Furthermore, it simplifies the manufacturing of the exhaust valve, as contours for sliding a slide do not need to be created, and corresponding (machining) post-processing of the base body is unnecessary. In the simplest case, the base body is preferably a pre-formed and / or die-cut component.

[0029] Furthermore, the support element is designed to place the valve element on the sealing edge in a corresponding manner.

[0030] To lift the valve element from the sealing edge, the support element preferably engages on the side or underside of the valve element facing the sealing edge, and particularly preferably on the spherical surface or spherical section of the valve element. The support element holds the valve element in such a way that the spherical surface or spherical section of the valve element rests on the sealing edge when the exhaust valve closes. The support element is preferably a rigid, one-piece component that, in the simplest case, engages directly with the valve element.

[0031] Furthermore, the support element preferably has a continuous recess or a through-opening for mounting the valve element in the support element and / or for the support element to engage with the valve element. Preferably, the through-opening is completely closed, so that the support element engages the valve element around its entire circumference and thus holds it securely. The inner wall of the through-opening or the through-opening of the support element is preferably circular and / or rotationally symmetrical and / or has a larger diameter than the sealing edge. Preferably, the through-opening for mounting the valve element is shaped correspondingly to the valve element, in particular conical, spherical, and / or rotationally symmetrical.

[0032] The valve element is moved, for example linearly or arcuately, along a travel path (valve element travel path) predetermined solely by the support element (and the sealing edge) to open and close the outlet valve or outlet opening. Preferably, the support element is tiltably mounted on the base body and tilts upon actuation, resulting in an arcuate travel path. This allows for a simple design of the support element and its actuation mechanism, as described below.

[0033] Another aspect of the invention is based on the understanding that the pressure conditions at the exhaust valve or the exhaust opening advantageously result in a centering effect for the valve element at the exhaust opening, which allows for a simple design of the support element and reliable closure of the exhaust opening. This centering effect is promoted by an advantageous design of the sealing edge, valve element, and / or support element. The support element is preferably connected to the valve element exclusively by a positive fit and / or is not fixed and / or detachable. The support element has a predetermined travel path (support element travel path) at the end of which, on the sealing edge side, the valve element is guided with play or loosely, or is placed with play on the sealing edge. When the exhaust opening closes, the support element continues to move towards the sealing edge after the valve element has been placed there.At the sealing-edge end of the carrier element's travel path, the valve element thus completely or partially disengages from its bearing or the through-opening in the carrier element, or from the (exclusively) positive-locking connection with the carrier element, so that the carrier element is configured to place the valve element on the sealing edge with play, in particular with radial play, that is, with radial clearance, especially preferably in all radial directions (perpendicular to the valve axis). In other words, when placed on the sealing edge, the valve element completely or partially separates from the carrier element and, at the sealing-edge end of the carrier element's travel path, is no longer engaged with the carrier element (completely and / or circumferentially) and is radially spaced from it (preferably completely circumferentially).The radial clearance of the valve element placed on the sealing edge is preferably in the range between 0.1 mm and 2 mm, particularly preferably between 0.5 mm and 1 mm, and is, for example, 0.1 mm, 0.2 mm, 0.3 mm, 0.5 mm, 0.8 mm, 1.0 mm, 1.2 mm, 1.5 mm or 2.0 mm, where each of the mentioned values ​​can also represent an upper or lower limit of the mentioned value ranges.

[0034] In the simplest case, the exhaust valve provides only the support element for the mechanical actuation of the valve element.

[0035] In a preferred embodiment, the exhaust valve according to the invention further comprises a valve element return spring that presses the valve element towards the sealing edge or into the sealing seat and / or into the support element and / or engages (directly) with the valve element. This ensures that the valve element is securely held in the support element and that the exhaust valve closes securely, and supports the centering effect for the valve element resulting from the pressure conditions.

[0036] In a preferred embodiment, the exhaust valve according to the invention has at least or exactly one deflecting element for actuating or actively operating the carrier element, in particular a cam or a circular path element, or two cams of more or less identical design. The deflecting element is designed to convert a (continuous and / or constant) rotational movement into a periodic translational movement, which periodically actuates or operates the carrier element and periodically opens and closes the exhaust valve. The deflecting element is generally mounted on a shaft that rotates (during operation) or is intended to rotate, or on a drive and / or camshaft, and periodically actuates the carrier element. In the simplest case, the deflecting element is in direct or immediate engagement with the carrier element and / or slides on the carrier element.In this process, a cam generates predetermined radial deflections, that is, a predetermined deflection pattern radial to the camshaft. A circular path element generates predetermined axial deflections, that is, a predetermined deflection pattern axial to the shaft.

[0037] The support element preferably has a rest position into which it is forced by one or more return springs (and optionally by the intended pressure conditions), and from which the deflecting element deflects the support element when the support element is actuated. In the simplest case, only exactly one return spring is provided in the outlet valve, preferably the valve element return spring described above or a return spring that engages directly with the support element.

[0038] In a first alternative, the outlet opening is open in the rest position of the carrier element, and the outlet valve is closed by the (rotating) deflecting element upon actuation, thus placing the valve element onto the sealing edge. In a second alternative, the outlet opening is closed in the rest position of the carrier element, and the outlet valve is opened by the (rotating) deflecting element upon actuation, thus lifting the valve element from the sealing edge.

[0039] The deflecting element and the return spring(s) are preferably designed such that the deflecting element engages with the support element at all times, particularly under all intended pressure conditions and at all rotational positions and speeds of the shaft. This allows for quiet operation of the exhaust valve.

[0040] In the simplest case of the exhaust valve according to the invention, the valve element is actuated (mechanically) solely by the carrier element, meaning it is (actively and / or selectively) actuated, controlled, or driven. In the simplest case, the valve element is in (alternating) engagement only with the carrier element and the sealing edge, depending on the stroke or position of the valve element along its travel path. Alternatively, the valve element return spring described above also engages the valve element, thereby forcing the valve element into the carrier element and the sealing edge. However, the effect of this (passive) return spring does not constitute actuation of the valve element as defined in this document. This design of the exhaust valve leads to a rapid or complete opening of the exhaust port even with a small stroke or distance of the valve element from the sealing edge, since the exhaust valve is a poppet valve.

[0041] In a preferred embodiment, an axially movable, spring-loaded proportional slide is provided on the low-pressure side of the outlet valve. This slide is pressed against the valve element by a proportional slide return spring and actuated by the valve element, so that the proportional slide follows the valve element along a predetermined travel path (proportional slide travel path). The proportional slide is arranged completely or partially within the outlet opening. The spring force of the proportional slide return spring is set (or sufficiently low) so that the proportional slide does not move the valve element (axially) or push it out of the support element, and / or so that the centering effect of the valve element on the sealing edge is not impeded. Preferably,The spring strength of the valve element return spring is less than the spring strength of the valve element return spring, meaning that the spring force of the valve element return spring is less than the spring force of the proportional slide return spring at every point of the proportional slide travel path.

[0042] The proportional slide engages the valve element along its predetermined travel path, preferably directly and / or exclusively by contact and / or positive locking, preferably at a continuous circumferential engagement area of ​​the proportional slide. The proportional slide travel path represents at least a portion of the valve element travel path and begins at the position where the valve element rests on the sealing edge, i.e., at a valve element stroke of zero.

[0043] The proportional slide valve enables proportional operation of the outlet valve along its entire travel range, or at least at the beginning of its travel range. In this operation, the (effective) fluid flow area of ​​the outlet opening and / or the fluid flow through the outlet valve increases continuously, preferably proportionally to the stroke of the valve element. Accordingly, the proportional slide valve is designed such that it (possibly together with the valve element) completely or substantially completely closes the outlet opening at the beginning of its travel range. This results in a predetermined high flow resistance at low valve element strokes (or when the valve element has just lifted from the sealing edge), and / or a small or zero fluid flow area, and / or no or only a small fluid flow through the outlet opening.The proportional slide valve is structurally designed in such a way that it provides the described proportional operation with increasing stroke of the valve element or when moving along the proportional slide valve's travel path. For example, the proportional slide valve has a funnel-shaped end at its valve element-side end.

[0044] In the simplest case, the proportional slide's travel path can correspond to or be identical with the valve element's travel path, so that the proportional slide engages the valve element at every point along its path. Preferably, however, the proportional slide's travel path represents only a (first) segment of the valve element's travel path and / or is shorter than the valve element's travel path. At the end of its travel path, the proportional slide preferably abuts a stop and no longer follows the valve element with increasing stroke and / or is no longer engaged with the valve element, so that the valve element is lifted away from the proportional slide by the support element. This allows the outlet opening to its maximum extent.

[0045] The stop against which the proportional slide abuts at the end of its travel can be designed, for example, as a protrusion in the base body, in the outlet opening, and / or in the proportional slide itself. Preferably, the base body is designed as a flat base plate, and the stop is designed as a rearward, i.e., spaced apart from the valve element or the valve element-side end of the proportional slide, radial and / or circumferential protrusion in the proportional slide, which abuts at the end of the proportional slide's travel on the side or surface of the base plate facing away from the valve element.

[0046] The present invention relates to an outlet valve with (exactly) one outlet opening and a distributor valve comprising a plurality N of the outlet valves described above, for example, 2, 3, 4, 6, or 8 outlet valves. Accordingly, the distributor valve typically has (exactly) one fluid inlet and a plurality of fluid outlets for the fluid to be distributed, each of which, in the simplest case, is assigned exactly one outlet valve. In general, the outlet valves of the plurality of outlet valves can be configured differently, in particular having different diameters of the outlet opening and / or the valve element. Preferably, the outlet valves of the plurality of outlet valves are all identical. Furthermore, a common base body, in particular a common and / or flat base plate, is preferably provided for the plurality of outlet valves, so that the outlet openings of all outlet valves are identical.All outlet openings of the distributor valve are arranged in the common base plate. The outlet valves are preferably individually or independently controllable.

[0047] In a preferred embodiment, the distributor valve has (exactly) one rotating shaft or drive shaft (during operation) for actuating the plurality of outlet valves or their support elements by means of one or more deflection elements as described above. The plurality N of outlet valves is assigned to exactly one shaft.

[0048] In a first embodiment, the shaft is designed as a camshaft. Several cams are attached to the shaft as deflection elements, rotating synchronously or at the same speed. Such a shaft or camshaft is preferably arranged horizontally or parallel to the base body or the flat base plate, and / or the exhaust valves of the plurality of exhaust valves are preferably arranged linearly or in a row side by side along the camshaft on the base body. In the simplest case, exactly one cam is provided per exhaust valve, and the shaft has N cams accordingly. Alternatively, two cams are provided per exhaust valve, and the shaft has 2xN cams, which are preferably identical. This promotes a uniform force transmission to the exhaust valves. The cams are preferably in direct or indirect contact with the carrier elements of the respective associated exhaust valves.direct intervention and / or sliding on it. In this variant, the exhaust valves can be opened and closed, in particular with identical period durations and different movement or deflection patterns.

[0049] In a second, alternative embodiment, exactly one or at least one circular track element is attached to the shaft as a deflection element. The shaft is preferably perpendicular to the base body or the flat base plate, and the plurality of exhaust valves are arranged around the shaft, preferably regularly or rotationally symmetrically with N-fold rotational symmetry. In this embodiment, the exhaust valves can be opened and closed with a phase shift, particularly with identical periods and identical movement or deflection patterns.

[0050] The present invention further relates to a distributor valve assembly comprising a first and a second shaft or drive shaft, which are coupled to each other via a coupling unit, for example via a gearbox or transmission, wherein preferably the second shaft is actuated or driven by the first shaft. Both shafts are arranged in different, preferably adjacent, sections or construction sections of the distributor valve assembly, which simplifies the mechanical coupling of the shafts.

[0051] Preferably, both construction sections are each designed as a distributor valve, such that a first distributor valve comprises a first plurality NI of outlet valves and a second distributor valve comprises a second plurality N2 of outlet valves. The distributor valve assembly preferably further comprises a one-piece or single-piece, flat base plate as a common base body for both construction sections or both distributor valves. In the simplest case, all outlet valves arranged on the common base plate are thus actuated either by the first or the second shaft and / or are arranged in the first or second construction section and / or assigned to the first or second shaft.

[0052] Preferably, the two shafts of the distributor valve group are coupled to each other such that the rotational speeds of the first and second shafts are the same or different and are in a predetermined fixed ratio or in an adjustable ratio to each other, in particular in the ratio 1:4, 1:3, 1:2, 2:3, 1:1, 3:2, 2:1, 3:1 or 1:4, and / or

[0053] - that the first shaft drives the second shaft in a first direction of rotation and does not drive it in a second, opposite direction of rotation, so that the first shaft rotates freely in the second direction. The gearbox is therefore preferably designed as a freewheel.

[0054] Alternatively, in one of the two sections of the distributor valve assembly, a (simple) outlet valve with a shaft is provided instead of the distributor valve. In another alternative, a (simple) outlet valve with a shaft is provided in each of the two sections of the distributor valve assembly. Accordingly, the distributor valve assembly then comprises two outlet valves with coupled shafts. Furthermore, the distributor valve assembly can also have additional sections designed as outlet valves or distributor valves, whose shafts are coupled. In a preferred embodiment of the distributor valve assembly, the coupling unit has a free rotation range of at least 180°, 270°, 300°, or 330° and less than 360°. For this purpose, the coupling unit has opposing axial end regions, for example, flat end faces of the first and second shafts, each with one or two...The shaft features a (fully) eccentric projection, for example, in the form of a pin or a conical rib, positioned at a specific distance from the shaft axis. The eccentric projections on the respective axial end regions are designed to engage or abut each other in both directions of rotation and to disengage when the direction of rotation changes. This ensures that, when the direction of rotation changes, the first shaft rotates freely for a predetermined angular range, the aforementioned free rotation range, while the second shaft remains stationary. This allows for the targeted approach and adjustment of predetermined rotational positions of the first and second shafts, thereby enabling the setting and / or maintenance of predetermined opening states of the various exhaust valves.In this case, both eccentric protrusions are preferably identical and / or designed as truncated cones, with (flat) side surfaces extending radially to the shaft, so that the truncated cones engage against each other over a flat surface.

[0055] BRIEF DESCRIPTION OF THE FIGURES

[0056] The invention is described below with reference to the accompanying drawings. The drawings are merely schematic representations and the invention is not limited to the specific embodiments shown.

[0057] Figure 1 shows a first embodiment of a distributor valve,

[0058] Figure 2 shows a second embodiment of a distributor valve,

[0059] Figures 3A, 3B, 3C show a first implementation example of an exhaust valve in different opening states,

[0060] Figures 4A, 4B, 4C show different variants of the sealing edge,

[0061] Figure 5 shows one variant of the valve element, Figure 6 shows a second embodiment of an exhaust valve,

[0062] Figure 7 shows an example of a distributor valve assembly, and

[0063] Figure 8 shows an axial end region of a coupling unit.

[0064] Figures 9A, 9B, 9C show different states of the coupling unit.

[0065] DETAILED FIGURE DESCRIPTION

[0066] Figure 1 shows a distributor valve 2 with two exhaust valves 1. Each exhaust valve 1 has a valve element 11 for closing an exhaust port 12. The valve element 11, which in this case is designed as a ball or ball valve element, corresponds to a sealing edge 13 of the exhaust port 12. The valve element 11 is actuated by a carrier element 14, which in the illustrated embodiment surrounds the valve element 11 and engages the underside of the valve element 11 on the sealing edge side. In the illustrated embodiment, the carrier elements 14 of the two exhaust valves 1 are tiltably arranged on a common base plate 15 and can be individually controlled. The actuation of the carrier elements 11 is effected by a camshaft 16, on which two (identical) cams 16a are provided for each exhaust valve 1.The cams 16a act as deflection elements for actuating the carrier elements 14, which generate variable radial deflections relative to the camshaft 16. In the embodiment shown in Figure 1, the rest position of the carrier elements 14 of the exhaust valves 1 is the open position, which is achieved by return springs (not shown). Accordingly, the cams 16a actuate the carrier elements 14 such that the actuated carrier element 14 moves towards the exhaust opening 12 and, to close the exhaust valve 1, places the valve element 11 on the sealing edge 13.

[0067] Figure 2 shows a variant of the distributor valve 2 with a common base plate 15 on which the drive shaft 16 is mounted perpendicularly. A circular track element 16b is arranged on the drive shaft 16, which has a circumferential shoulder as a sliding surface with different axial heights. The sliding surface of the circular track element 16b engages the support elements 14 of the two outlet valves 1 and lifts them from the outlet opening 12 or the sealing edge 13, so that the outlet valve 1 is opened upon actuation. The rest position of the support elements 14 or the outlet valves 1 is, in this case, the closed position. Figures 3A, 3B, and 3C show an outlet valve 1 in different opening states. In Figure 3A, the outlet valve 1 is shown in the closed state.The two cams 16a mounted on the camshaft 16 actuate the carrier element 14 from a rest position, such that the carrier element 14 moves towards the base plate 15 and places the valve element 11 onto the sealing edge 13 of the exhaust port 12 with clearance. The predetermined travel path of the tilting carrier element is arc-shaped and extends towards the base plate 15 beyond the point at which the valve element 11 engages with the sealing edge 13 and closes the exhaust port 12. Accordingly, after the valve element 11 has been placed on the sealing edge 13, the carrier element 14 continues to move towards the base plate 15, so that the valve element 11 disengages from the positive-locking connection with the carrier element 14. This creates a radial clearance 18 between valve element 11 and support element 14 such that valve element 11 and support element 14 no longer touch each other or are no longer in engagement with each other.

[0068] With a smaller radial deflection of the cams 16a, the support element 14 moves away from the outlet opening 12 and lifts the valve element 11 away from the sealing edge 13, as shown in Figures 3B and 3C.

[0069] Figure 3A further shows a spring-loaded proportional slide 17 with a return spring 17a that presses the proportional slide 17 against the valve element 11. When the valve element 11 rests on the sealing edge 13, the valve element 11 actuates the proportional slide 17 and moves it linearly along the valve axis 1a by engaging a circumferential engagement area of ​​the proportional slide 17 on the valve element side. The spring force of the return spring 17a of the proportional slide 17 is set accordingly low.

[0070] When the outlet valve 1 opens, the support element 14 lifts the valve element 11 from the sealing edge 12, as shown in Figure 3B, and the proportional slide 17 follows the valve element 11, so that the circumferential engagement area of ​​the proportional slide 17 remains engaged with the valve element 11. With increasing stroke or travel distance of the valve element 11 and proportional slide 17, an increasing fluid flow area is released in the outlet opening 12, thus achieving proportional operation of the outlet valve 1. After a predetermined travel distance, the proportional slide 17 abuts the underside of the base plate 15 facing away from the sealing edge 13 with a rear stop 17b, so that with a further increasing stroke, the valve element 11 also lifts off the proportional slide 17, thus maximally releasing the outlet opening 12.

[0071] Figures 4A, 4B, and 4C show different configurations of the sealing edge 13. In Figure 4A, the sealing edge 13 is configured as a sealing edge 13a, as shown in the previous figures. In an alternative configuration, however, the sealing edge 13 is configured as a sealing seat 13b with a seating surface that extends perpendicular to the direction of rotation of the sealing edge 13 or the outlet opening 12.

[0072] In the variant shown in Figure 4B, the sealing edge 13 is designed as a conical sealing seat 13b, resulting in an internal cone.

[0073] In the variant shown in Figure 4C, the sealing edge 13 is designed as a spherical or ball-shaped sealing seat 13b. This spherical sealing seat 13b is created using an embossed ball. Furthermore, the spherical sealing seat 13b has exactly one, i.e., a constant, radius of curvature. The radius of curvature of the sealing seat 13b is larger than the radius of curvature of the sealing edge 13 and also slightly larger than the radius of curvature of the ball valve element 11. This facilitates centering of the valve element 11, which rests with clearance on the sealing seat 13b, and thus promotes sealing of the outlet opening 12.

[0074] Figure 5 shows a variant of the valve element 11 which is not completely spherical, i.e., not a ball valve element, but only partially spherical with a spherical surface section 11b in an annular area corresponding to the sealing edge 13. This variant also supports the centering of the valve element 11 placed on the sealing edge 13 or the sealing seat 13b.

[0075] Figure 6 shows a variant in which a valve element return spring 11 pushes the valve element 11 towards the outlet opening 12, the sealing edge 13, and the support element 14. This ensures that the valve element 11 is securely held in the support element 14 and prevents it from unintentionally detaching from the support element 14. Figure 7 shows a distributor valve assembly 3, consisting of two distributor valves 2, whose camshafts 16', 16" are coupled via a coupling unit in the form of a gearbox 19. This results in different rotational speeds of the camshafts 16', 16" of the two distributor valves 2.

[0076] Figures 8 and 9A to 9C show an alternative embodiment of the coupling unit 19 for the distributor valve group 3. The coupling unit 19 has opposing axial end regions 16c on the first and second shafts 16', 16" respectively.

[0077] Figure 8 shows the axial end region 16c of the first shaft 16'. The axial end region 16c of the second shaft 16" is identically designed. The axial end region 16c, or the axial end of the shaft 16', has a flat end face 16c with an eccentric projection 16d, which is designed as a symmetrical truncated cone. The truncated cone 16d has flat side surfaces that extend radially to the shaft axis 16e. In the coupling unit 19, the axial end regions 16c of the first and second shafts 16', 16" are arranged opposite each other, so that the truncated cones 16d engage against each other over a flat surface at their side surfaces, and the first shaft 16' can drive the second shaft 16" to, for example, approach and, if necessary, maintain predetermined rotational positions of the shafts 16', 16". The cone truncated section 16d forms a completely eccentric elevation, which is arranged away from the shaft axis 16e.

[0078] Figures 9A to 9C show various operating states of this coupling unit 19 in a top view of the axial end regions 16c. In Figure 9A, the conical truncations 16d are in contact with each other at their side surfaces, and the first shaft 16' drives the second shaft 16" counterclockwise. In Figure 9B, the second shaft 16" has reached a predetermined rotational position. The first shaft has changed its direction of rotation and rotates freely clockwise (rotation angle still within the free rotation range, which in this case is 330°), meaning that the conical truncation 16d of the first shaft 16' does not (yet) contact the conical truncation 16d of the second shaft 16'. In Figure 9C, the truncated cone 16d of the first shaft 16' abuts (on the opposite side or surface) the truncated cone 16d of the second shaft 16" and drives the second shaft 16" clockwise. [List of reference symbols]

[0079] 1 exhaust valve

[0080] la Valve axis

[0081] 2 distributor valve

[0082] 3 Distributor valve group

[0083] 11 Valve element, ball valve element

[0084] 1 la Valve element return spring

[0085] 11b Spherical surface section

[0086] 12 Outlet opening

[0087] 13 Sealing edge

[0088] 13a Sealing edge

[0089] 13b Sealing seat

[0090] 14 Support element

[0091] 15 Base plate, base body

[0092] 16, 16', 16" camshaft, drive shaft, shaft 16a cam

[0093] 16b Circular path element

[0094] 16c axial end region, end face

[0095] 16d eccentric elevation, conical truncation 16e shaft axis

[0096] 17 proportional sliders

[0097] 17a Return spring

[0098] 17b attack

[0099] 18 radial play, radial play

[0100] 19 coupling unit, gearbox

Claims

PATENT CLAIMS 1. Exhaust valve (1) comprising - an outlet opening (12) with a sealing edge (13), - a valve element (11) corresponding to the sealing edge, and - a support element (14) which is designed to lift the valve element from the sealing edge and to place it on the sealing edge, preferably with clearance.

2. Outlet valve (1) according to claim 1, wherein the valve element (11) and the support element (14) are arranged on a high-pressure side of the outlet valve.

3. Outlet valve (1) according to one of the preceding claims, wherein the sealing edge (13) is designed as a sealing edge (13a) or as a conical sealing seat (13b) or as a spherical sealing seat (13b), which is preferably created by pressing in an embossing ball.

4. Outlet valve (1) according to one of the preceding claims, wherein the valve element (11) is a ball valve element or at least is designed as a spherical surface section (11b) in a ring area corresponding with the sealing edge (13).

5. Outlet valve (1) according to claims 3 and 4, wherein the spherical sealing seat has a radius of curvature that is equal to or greater than a radius of curvature of the ball valve element (11) or of the spherical surface section (11b) of the valve element, preferably in the range between 1% and 20%.

6. Outlet valve (1) according to one of the preceding claims, wherein - the support element (14) is configured to lift the valve element (11) from the sealing edge (13) at a predetermined lifting angle, which is preferably less than 20°, 15°, 10°, 5°, 2° or 1° or is 0°, and / or - the carrier element has a through-opening, preferably a closed through-opening, for engagement with the valve element, and / or - the support element is connected to the valve element exclusively by a form-fit connection and / or is not permanently and / or detachably connected, and / or - the carrier element has a predetermined travel path, at the sealing-edge-side end of which the valve element is placed on the sealing edge and / or is completely or partially released from the positive-locking connection, and / or - the valve element has a radial clearance (18) in the range between 0.1 mm and 2 mm at the sealing-edge-side end of the travel path of the carrier element and / or is spaced circumferentially from the carrier element, and / or - the support element is tiltable.

7. Exhaust valve (1) according to one of the preceding claims, comprising a valve element return spring (11a) which forces the valve element (11) into the sealing rim (13) and / or the support element (14).

8. Exhaust valve (1) according to one of the preceding claims, comprising a deflecting element, in particular a cam (16a) or a circular track element (16b), for periodically actuating the carrier element (14) and / or for deflecting the carrier element from a rest position.

9. Outlet valve (1) according to one of the preceding claims, wherein the valve element (11) is actuated exclusively by the carrier element (14).

10. Outlet valve (1) according to one of the preceding claims, comprising a proportional slide (17), - which is axially movable and / or spring-loaded, and / or - which is moved by the valve element (11) along a predetermined travel path, wherein the travel path of the proportional slide preferably corresponds to a partial section of the travel path of the valve element, and / or - which creates a proportional operation along part of its travel path or along its entire travel path, and / or - which has a radial protrusion (17b) spaced apart from the valve element in the proportional slide as a stop.

11. Exhaust valve (1) according to one of the preceding claims, comprising a shaft (16) on which the deflecting element (16a, 16b) is preferably attached.

12. Distributor valve (2) with a plurality of outlet valves (1) according to one of the preceding claims, wherein preferably - the exhaust valves are identical in design, and / or - the outlet openings of the outlet valves are arranged in a common base plate (15).

13. Distributor valve (2) according to claim 12, with a shaft (16) for actuating the plurality of exhaust valves (1), wherein preferably the shaft is designed as a camshaft and / or a plurality of cams (16a) are attached to the shaft, or wherein preferably a circular track element (16b) is attached to the shaft.

14. Distributor valve group (3) with - a first section which is configured as an outlet valve (1) according to claim 11 or as a distributor valve (2) according to claim 13, wherein its shaft (16) forms a first shaft (16') of the distributor valve group, and - a second section configured as an outlet valve according to claim 11 or as a distributor valve according to claim 13, wherein its shaft forms a second shaft (16") of the distributor valve group, wherein the first wave and the second wave are coupled to each other via a coupling unit (19) and / or the first wave actuates the second wave via the coupling unit, preferably - such that the rotational speeds are in a predetermined fixed ratio to each other, in particular in the ratio 1:4, 1:3, 1:2, 2:3, 1:1, 3:2, 2:1, 3:1 or 1:4, and / or - such that the first shaft drives the second shaft in a first direction of rotation and rotates freely in a second, opposite direction of rotation.

15. Distributor valve group (3) according to claim 14, wherein the coupling unit (19) - has a free rotation range of at least 180°, 270°, 300° or 330°, and / or - each has opposing axial end regions (16c) of the first and second shaft (16', 16") with each an eccentric protrusion ( 16d) which are designed to engage with each other in both directions of rotation and to disengage from each other when the direction of rotation changes.

Images