초록 ▼

A double seat valve in which a second closing element (4), in its closed position, rests with a stopping surface (4f) on a face of its cylindrical projection (4*) directly upon a first seat (2a) and, together with a peripheral wall (4c, 4h), forms a second wraparound edge (U2) upon an interface (2e,

A double seat valve in which a second closing element (4), in its closed position, rests with a stopping surface (4f) on a face of its cylindrical projection (4*) directly upon a first seat (2a) and, together with a peripheral wall (4c, 4h), forms a second wraparound edge (U2) upon an interface (2e, 2e*). The peripheral wall (4c), at its end facing away from a first closing element (3), merges into a rotationally symmetric reversing surface (4d) that leads to a face (4e) of a recess (4b) oriented essentially perpendicular to the longitudinal axis of the second closing element (4). In meridian section, the reversing surface (4b) has a contour (K) with a bend-free curve, a direction vector in the leading point of the reversing surface (4d) points into a discharge borehole (3d, 3d*) central in the first closing element (3) without colliding with the first closing element (3) in the vicinity of its areas bordering the leakage cavity (5) and forming dynamic pressure.

대표청구항 ▼

The invention claimed is: 1. Double seat valve comprising two valve housing parts (1a, 1b) and first and second closing elements (3, 4) arranged in series and movable with regard to each other, which prevent in a closed position of the double seat valve (1) fluids from one of the valve housing part

The invention claimed is: 1. Double seat valve comprising two valve housing parts (1a, 1b) and first and second closing elements (3, 4) arranged in series and movable with regard to each other, which prevent in a closed position of the double seat valve (1) fluids from one of the valve housing parts (la; lb) flowing into the other of the valve housing parts (1a, 1b), which define in the closed position, as well as in the open position, a leakage cavity (5) between them, which is connected with the surroundings of the double seat valve (1), wherein in the closed position the first closing element (3), which is formed as a slide piston, is received in sealing manner in a connecting opening (2c) connecting the valve housing parts (1a, 1b) with each other and which comes to abut, in a sealing manner in the course of its opening movement, the second closing element (4), which is associated with a second seat (2b), and the latter element is also transferred to an open position (H) during a further opening movement, the first closing element (3) comprising a first seal (6) at its end section (3*), which seals radially against a cylindrical first seat (2a) formed in the connecting opening (2c), the second closing element (4) comprising at its end facing towards the first closing element (3) a recess (4b) with a substantially cylindrical peripheral wall (4c) aligned with the cylindrical first seat (2a), and the recess being dimensioned in order to sealingly receive the end section (3*) and the radial first seal (6) of the first closing element (3) during the opening movement, before the second closing element (4) opens, each of the closing elements (3, 4) being able to be transferred independently from the other by a partial lift to a seat cleaning position in order to rinse its respective coaxial seat (2a, 2b), wherein the second closing element (4) can be transferred to its seat cleaning position by a second partial lift (T2) in the same direction as the opening movement and the first closing element (3) can be transferred to its seat cleaning position by a first partial lift (T1) in the direction opposed to the opening movement, a cylindrical lug (3*, 4*) being arranged at each closing element (3, 4) on the leakage cavity side, which forms an annular choke gap (D1, D2) with the associated connecting opening (2c), the first seat (2a) having a diameter that is smaller than the diameter of an annular recess (2d) associated with the second closing element (4) in the connecting opening (2c) , and a transition surface (2e) between the first seat (2a) and the annular recess (2d), characterised in that the second closing element (4) abuts in its closed position with a stop face (4f) arranged at a front face of the cylindrical lug (4*), which forms a second circumferential edge (U2) with the circumferential wall (4c; 4h), against the transition surface (2e; 2e*), and that directly adjacent to the first seat (2a), the circumferential wall (4c) at its end averted from the first closing element (3) merges into a rotationally symmetrical diversion area (4d) for a flow of cleaning fluid that has passed the first seat (2a), and this diversion area (4d) leads into a front face (4e) of the recess (4b) oriented substantially perpendicular to the longitudinal axis of the second closing element (4), and that, viewed in vertical center section, the diversion area (4d) comprises the contour (K) with an uncurved portion, wherein, in the seat cleaning position of the first closing element (3), a flowpath of a seat cleaning flow past the cylindrical first seat (2a) is directed into a flow inlet of the diversion area (4d), and a direction vector of a flow outlet of the diversion area (4d) points into a central discharge bore (3d; 3d*) arranged in the first closing element (3), without colliding with the first closing element (3) in the region of its areas bounding the leakage cavity (5) and without forming impact pressure. 2. Double seat valve according to claim 1, wherein a frontal boundary of the first closing element (3) directed towards the leakage cavity (5) has an axial safety distance (x) from a direction vector at an exit of the transition area (2e) formed as a first circumferential edge (U1) into the first seat (2a). 3. Double seat valve according to claim 2, wherein the safety distance (x) is at least as large as the sum of all production tolerances of the components of the double seat valve (1), which determine in the closed position of the first closing element (3) the smallest axial distance thereof to the transition area (2e). 4. Double seat valve according to claim 1, wherein the first circumferential edge (U1) formed by the transition area (2e) and the first seat (2a) is rounded with the smallest-possible first corner rounding (r3). 5. Double seat valve according to claim 1, wherein the annular recess (2d) forms an obtuse or a right first diversion angle (α) with the transition area (2e). 6. Double seat valve according to claim 5, wherein the recess (2d) comprises a rounded transition configured with a radius of curvature (r1) to the transition area (2e). 7. Double seat valve according to claim 1, wherein the cylindrical circumferential wall (4c) leads into an insertion slope (4h) in order to achieve a smooth transition of the radial first seal (6), and the insertion slope (4h) forms a second circumferential edge (U2) with the stop face (4f). 8. Double seat valve according to claim 1, wherein the second circumferential edge (U2) is rounded with a smallest possible second corner rounding (r4). 9. Double seat valve according to claim 1, wherein the diversion area (4d) undercuts the front face (4e) by an axial undercutting distance (y). 10. Double seat valve according to claim 1, wherein the contour (K) comprises a sequence of sections (K1, K2, . . . , Kn), that the first section (K1) and the third and last section (K3=Kn) leading out of the front face (4e) are each configured linear, and that these sections (K1, K3) are connected with each other through the second section (K2), which tangentially rounds the latter with a largest-possible diversion radius (r2). 11. Double seat valve according to claim 1, wherein the contour (K) comprises a sequence of bent sections (K1, K2, K3, . . . , Kn), which each have a common tangent at their respective transition points or that the contour (K) comprises a single section of continuously varying curvatures or that the contour (K) comprises a single section with constant curvature. 12. Double seat valve according to claim 1, wherein the direction vector of the last section (Kn) comprises a third diversion angle (β) with regard to the front face (4e) preferably in the range of 5 ≧β≧20 degrees, preferably β=15 degrees. 13. Double seat valve according to claim 1, wherein the discharge opening (3d*) connects the leakage cavity (5) with the surrounding of the double seat valve (1) through connecting bores (3d*) spaced around the circumference, and that the frontal boundary of the first closing element (3) directed towards the leakage cavity comprises a chamfer (3f) dropping circumferentially on all sides towards the discharge bore (3d*). 14. Double seat valve according to claim 1, wherein the discharge bore (3d*) connects the leakage cavity (5) with the surrounding of the double seat valve (1), that the frontal boundary of the first closing element (3) directed towards the leakage cavity (5) comprises a chamfer (3f) dropping circumferentially on all sides towards the discharge bore (3d), and that a first shifting rod (3a) connected with the first closing element (3) concentrically penetrates a second shifting rod (4a) connected with the second closing element (4) and configured as a hollow rod, continues flying through the discharge bore (3d) and is firmly connected with the first closing element at an end of the first closing element (3) averted from the second closing element (4) through a substantially radially oriented traverse (3e). 15. Double seat valve according to claim 14, wherein the chamfer (3f) is configured as an envelope of cone. 16. Double seat valve according to claim 15, wherein the envelope of cone is inclined with regard to the base of the cone by an angle of inclination (ζ) preferably in the range of 10 ≦ζ≦20 degrees, preferably ζ=15 degrees. 17. Double seat valve according to claim 16, wherein three traverses (3e) arranged equally spaced across the circumference are fixedly provided at a shifting rod section (3a*), which are each fixedly connected on the radial outside with a circumferential ring (3g), and that the shifting rod section (3a*), the traverses (3e) and the ring (3g) form an integral welding part (30). 18. Double seat valve according to claim 17, wherein the welding part (30) connects on the outside through the ring (3g) to a pressure balance piston (3c) bounding a section of the discharge bore (3d) remote from the leakage cavity and on the inside through the shifting rod section (3a*) to the first shifting rod (3a), and that the ring (3g) is enlarged in its inner diameter with regard to the diameter of the discharge bore (3d) with interposition of a conically expanding transition area such that the inner passage of the discharge bore (3d) is not narrowed by the traverses (3e) . 19. Double seat valve according to claim 1, wherein the second seat (2b) is configured cylindrical and formed by the annular recess (2d), and that the second closing element (4) comprises a second seal (7), which seals radially against the second seat (2b) in sliding engagement. 20. Double seat valve according to claim 19, wherein the second seat (2b) comprises a chamfered edge expanding towards the second closing element (4) for achieving a smooth transition of the radial second seal (7). 21. Double seat valve according to claim 20, wherein the chamfered edge is pitched with regard to the second seat (2b) by an angle of pitch preferably in the range of 7.5 to 15 degrees, preferably 10 degrees. 22. Double seat valve according to claim 20, wherein the chamfered edge expands at its end directed towards the second closing element (4) into an opening slope (2f), the latter being pitched with regard to the second seat (2b) by an opening angle preferably in the range of 35 55 degrees, preferably 45 degrees. 23. Double seat valve according to claim 1, wherein the second seat (2b) is configured conical and is inclined with regard to the cylindrical recess (2d) by a seat angle (γ), and that the second closing element (4) comprises a second seal (7), which seals axially/radially against the second seat (2b) in sliding/pressing engagement. 24. Double seat valve according to claim 23, wherein the seat angle (γ) is configured in the range of 25 ≦γ≦35 degrees, preferably γ=30 degrees. 25. Double seat valve according to claim 23, Wherein the second seat (2b) expands at its end directed towards the second closing element (4) into an opening slope (2f), the latter being pitched with regard to the cylindrical recess (2d) by an opening angle (φ), preferably in the range of 35 ≦φ≦55 degrees, preferably with φ=45 degrees. 26. Double seat valve according claim 1, wherein the second seat (2b) is arranged vertically to the longitudinal axis of the double seat valve (1), and that the second closing element (4) comprises a second seal (7), which seals axially against the second seat (2b) in pressing engagement. 27. Double seat valve according to claim 1, wherein an end section (4**) of the second cylindrical lug (4*) comprises an annular circumferential second chamfer (4g) radially on the outside following the stop face (4f), which extends from the stop face ((4f) at a chamfer angle (λ), and which is dimensioned such that a third circumferential edge (U3) formed by rounding between the second chamfer (4g) and the second diameter (d2) of the second cylindrical lug (4*) is shifted, viewed in radial direction, outwards as far as possible and as close as admissible to the shape of the transition area (2e) determined by the radius of curvature (r1) and forms an annular circumferential centering point (Z) there.