Diverter valve for conveying material to be conveyed and method for cleaning a diverter valve of this type

Abstract

A diverter valve for conveying material to be conveyed, the diverter valve being cleanable using a method for CIP cleaning, comprises a housing with at least three passage openings to feed or discharge the material to be conveyed, the passage openings defining a conveying plane. The diverter valve further comprises a rotary part having an axis of rotation and an outer contour designed conically in relation to the axis of rotation at least in sections, the rotary part being arrangeable in the housing in a sealed manner, the rotary part being displaceable along the axis of rotation in an axially driven manner and being arranged such as to be drivable for rotation about the axis of rotation, the axis of rotation being oriented perpendicular to the conveying plane, a passage duct arranged in the rotary part, which—depending on a rotary position of the rotary part—connects in each case two passage openings for conveying material along the passage duct through the diverter valve. The CIP cleaning method of a diverter valve of this type comprises the pulling back and rotating the rotary part into an intermediate position to clean and then dry the diverter valve intensively. A particular feature is the embodiment configured without drainage in the housing of the diverter valve.

Claims

1. A diverter valve for conveying material to be conveyed, comprising: a housing with at least three passage openings to one of feed and discharge the material to be conveyed, the passage openings defining a conveying plane, a rotary part having a rotary axis and an outer contour designed conically at least in sections relative to the axis of rotation, the rotary part being arrangeable in the housing in a sealed manner, the rotary part being displaceable along the axis of rotation in an axially driven manner and being arranged such as to be drivable for rotation about the axis of rotation, the axis of rotation being oriented perpendicular to the conveying plane, and a passage duct arranged in the rotary part, the passage duct connecting, depending on a rotary position of the rotary part, in each case two passage openings to convey material to be conveyed through the diverter valve along the passage duct, and passage duct sealing members arranged circumferentially on the rotary part in relation to a passage duct longitudinal axis, wherein the passage duct sealing members are each retained in a sealing groove of the rotary part in such a way as to be clamped against a surface of the rotary part, wherein the passage duct sealing members protrude from the outer contour of the rotary part with a protruding section, wherein the protruding section has at least one transition chamfer for a smooth transition of the surfaces of the rotary part and the passage duct sealing member.

2. The diverter valve as claimed in claim 1, comprising a rotary drive for rotatably displacing the rotary part about the axis of rotation, the rotary drive enabling a central position of the rotary part.

3. The diverter valve as claimed in claim 1, wherein a cone angle of the outer contour of the rotary part is between 10° and 40°.

4. The diverter valve as claimed in claim 1, wherein the rotary part is in direct contact, with its outer contour, with the inner contour of the housing.

5. The diverter valve as claimed in claim 1, further comprising: cone sealing members arranged circumferentially on the rotary part in relation to the axis of rotation, the passage duct being arranged between the cone sealing members in relation to the axis of rotation.

6. The diverter valve as claimed in claim 1, wherein the passage duct sealing members are each retained in a sealing groove of the rotary part in such a way as to be clamped against a surface of the rotary part without gaps.

7. The diverter valve as claimed in claim 1, wherein the passage duct sealing members are each retained in the corresponding sealing groove in a form-fitting manner.

8. The diverter valve as claimed in claim 1, wherein the transition chamfer is circumferential.

Description

BRIEF DESCRIPTION OF THE DRAWING

(1) FIG. 1 shows a perspective view of a three-way diverter valve;

(2) FIG. 2 shows a simplified principle view of the installation of the diverter valve with a horizontal passage direction and an outlet towards the bottom;

(3) FIG. 3 shows a view, corresponding to FIG. 2, with a horizontal passage direction and an outlet towards the top;

(4) FIG. 4 shows a view, corresponding to FIG. 2, with a vertical passage direction and an outlet towards the top;

(5) FIG. 5 shows a view, corresponding to FIG. 2, of the diverter valve with a vertical passage direction and an outlet towards the bottom;

(6) FIG. 6 shows an exploded view of the diverter valve in FIG. 1;

(7) FIG. 7 shows another perspective view of the diverter valve as shown in FIG. 1, the housing being shown in a partly cut view;

(8) FIG. 8 shows a sectional view along section line VIII-VIII in FIG. 1 with the diverter valve in an outlet arrangement;

(9) FIG. 9 shows a sectional view, corresponding to FIG. 8, of the diverter valve in a passage arrangement;

(10) FIG. 10 shows a longitudinal sectional view, relative to the conveying direction, of the diverter valve in the passage arrangement;

(11) FIG. 11 shows a cross-sectional view, relative to the conveying direction, of the diverter valve in a rinsing arrangement;

(12) FIG. 12 shows a sectional view, corresponding to FIG. 10, of another embodiment of the diverter valve, the rotary part having passage duct sealing members;

(13) FIG. 13 shows an enlarged detail view of the passage duct sealing member as shown in FIG. 12;

(14) FIG. 14 shows a perspective view of a rotary part of the diverter valve as shown in FIG. 12;

(15) FIG. 15 shows a view, corresponding to FIG. 10, of a diverter valve according to another embodiment where the rotary part is in direct contact, with its outer contour, with an inner contour of the housing;

(16) FIG. 16 shows a sectional view, corresponding to FIG. 2, of a diverter valve with the rotary part in an intermediate rotary position for cleaning with a large axial gap in a CIP rinsing position;

(17) FIG. 17 shows a perspective view of a rotary part with a breakthrough;

(18) FIG. 18 shows a sectional view of a diverter valve with the rotary part as shown in FIG. 17;

(19) FIG. 19 shows a view, corresponding to FIG. 17, of a rotary part according to another embodiment with a kidney-shaped breakthrough;

(20) FIG. 20 shows a sectional view of a rotary part according to another embodiment with a double-conical breakthrough;

(21) FIG. 21 shows a view, corresponding to FIG. 19, of a rotary part according to another embodiment configured as a segment component;

(22) FIG. 22 shows a sectional view of the rotary part as shown in FIG. 21;

(23) FIG. 23 shows a view of the rotary part in FIG. 21 according to arrow XXIII;

(24) FIG. 24 shows a view, corresponding to FIG. 9, of a diverter valve according to another embodiment with passage duct sealing members configured in another way;

(25) FIG. 25 shows an enlarged sectional view of a sealing groove of the diverter valve as shown in FIG. 24;

(26) FIG. 26 shows an enlarged sectional view, corresponding to FIG. 25, with the passage duct sealing member being inserted;

(27) FIG. 27 shows a view, corresponding to FIG. 26, of another embodiment of the passage duct sealing member.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

(28) A diverter valve 1 shown in FIG. 1 to FIG. 11 serves to convey material to be conveyed. The material to be conveyed is for example bulk material, in particular particulate and/or powdery material such as plastic pellets or particulate and/or powdery food. The bulk material is conveyed in particular pneumatically. The material to be conveyed can also be a pasty mass and/or liquid, in other words a fluid.

(29) The diverter valve 1 is configured as a three-way diverter valve. The diverter valve 1 has a housing 2 provided with a first passage opening 3, a second passage opening 4 and a third passage opening 5. The passage openings 3, 4, 5 serve to feed and/or discharge the material to be conveyed. The passage openings 3, 4, 5, in particular the central lines of the passage openings 3, 4, 5, define a conveying plane.

(30) A rotary part 6 is arranged in the housing 2. The rotary part 6 has an axis of rotation 7 oriented perpendicular to the conveying plane. The rotary part 6 is arranged in the housing 2 such as to be axially displaceable along the axis of rotation 7. The initial adjustment of the gap between the outer contour 9 of the rotary part 6 and the inner contour 17 of the housing 2 is performed by setting the axial position of the rotary part 6 in the housing 2. In the embodiment shown, said gap adjustment is performed using a threaded sleeve 32, which enables an infinitely variable, in other words continuous axial displacement of the rotary part 6 in the housing 2 from outside the housing 2 by means of a tool, for example. The rotary part 6 is arranged in the housing 2 such as to be rotatable about the axis of rotation 7.

(31) The rotary part 6 has a passage duct 8. The rotary part 6 is in particular arrangeable in an outlet arrangement shown in FIG. 9 in which the first passage opening 3 is directly connected to the third passage opening 5 via the passage duct 8. In the outlet arrangement, the second passage opening 4 is sealed by the rotary part 6. In other words, the three-way diverter valve 1 ensures that in the outlet arrangement, the passage openings 3, 5 are connected to each other to allow material to be conveyed along an outlet direction 41 while the passage opening 4 is shut off by the rotary part 6.

(32) Correspondingly, FIG. 10 shows a passage arrangement in which the first passage opening 3 is connected to the second passage opening 4 via the passage duct 8 to convey material along a passage direction 42. The passage direction 42 is linear between the first passage opening 3 and the second passage opening 4. The first passage opening 3 and the second passage opening 4 are arranged essentially opposite, in particular diametrically opposite, one another on the housing 2. The third passage opening 5 is sealed by the rotary part 6. The outlet direction 41 from the first passage opening 3 to the third passage opening 5 is arranged at an outlet angle β in relation to the passage direction 42 between the first passage opening 3 and the second passage opening 4. In the exemplary embodiment shown, the outlet angle β is 45°. It is advantageous if the outlet angle β is between 30° and 90°, in particular between 40° and 60°, and in particular between 42° and 50°.

(33) The rotary part 6 is configured essentially frustoconically in relation to its axis of rotation 7, in other words it has a conical outer contour 9 at least in sections along the axis of rotation 7. In the illustration of FIG. 6, the axis of rotation is the explosion axis. The passage duct 8 is oriented perpendicular to the axis of rotation 7. The passage duct is arranged eccentrically on the rotary part 6 in relation to the axis of rotation 7.

(34) The frustoconical geometry of the rotary part 6 is defined by a larger front end face 10 and a smaller front end face 11. In the exemplary embodiment shown, the front end faces 10, 11 are each oriented perpendicular to the axis of rotation 7 and configured in a planar manner. Also, the front end faces 10, 11 may each have a convex shape and in particular be inclined and/or curved at least in sections.

(35) On the larger front end face 10, an axial drive shaft 12 is fastened to the rotary part 6. The axial drive shaft 12, which is guided out of the housing 2 via a first opening 13 in a housing cover 14, is connected to an axial drive 15 via a coupling 47. The axial drive 15 is configured as a pneumatic drive, in particular a pneumatic cylinder, in particular as a lift drive. The axial drive 15 may also be configured as an electric motor or as a hydraulic cylinder. The axial drive 15 enables a driven axial displacement of the rotary part 6 in the housing 2 along the axis of rotation 7. The axial drive 15 can be designed such as to have an intermediate position, which allows the rotary part 6 to be displaced in the housing 2 along the axis of rotation 7 into an axial intermediate position. In the axial intermediate position of the rotary part 6 in the housing 2, the diverter valve 1 can be operated and/or rotated with a small gap of between 0.01 mm and 0.5 mm.

(36) The coupling 47 provides a connection, directed in the axial direction of the axis of rotation 7, between the axial drive 15 and the axial drive shaft 12 in order to transmit axial forces. The coupling 47 is free of torque in relation to the axis of rotation 7. A rotary movement of the rotary part 6 is not transmitted to the axial drive 15 by the coupling 47. To this end, the coupling 47 of the exemplary embodiment shown has a sleeve-shaped design with an annular collar 48 facing the axial drive shaft 12 and directed radially inwardly. In the axial direction of the rotary axis 7, the annular collar 48 engages behind an annular disc section 49 of the axial drive shaft 12. The annular disc section 49 is arranged rotatably in the sleeve section of the coupling 47. The annular disc section 49 is formed in one piece with the axial drive shaft 12 and is arranged at the front end of the axial drive shaft 12.

(37) The rotary part 6 is provided with two cone sealing members 16, which are arranged on the rotary part 6 such as to be spaced from one another in relation to the axis of rotation 7. According to the exemplary embodiment shown, the cone sealing members 16 are each configured as O-rings. The cone sealing members 16 serve to seal the cone surface, in other words the conical outer contour 9, against the corresponding inner contour 17 of the housing 2.

(38) The cone sealing members 16 are each arranged adjacent to the larger front end face 10 or the smaller front end face 11, respectively. In particular, the passage duct 8 is arranged along the axis of rotation 7 between the two cone sealing members 16.

(39) On the smaller front end face 11, a rotary drive shaft 18 is fastened to the rotary part 6, which is in particular formed in one piece with the housing main body 21, said rotary drive shaft 18 being configured to be guided out through a second opening 19 in the housing bottom 20. The rotary drive shaft 18 has a torque transmitting section 22 at least in sections along the axis of rotation 7, said torque-transmitting section 22 being non-round in the plane perpendicular to the axis of rotation 7 and having an external square geometry in the exemplary embodiment shown. By means of the torque transmitting section 22, the rotary drive shaft 18 can be coupled to a rotary drive 23 in a torque-transmitting manner. The rotary drive 6 can be driven in the housing 2 for rotation in relation to the axis of rotation 7. The rotary drive 23 is configured as a pneumatic rotary drive. The rotary drive 23 can also be configured as an electric motor, hydraulic motor or hydraulic cylinder. The rotary drive 23 enables a rotation of the rotary part 6 between the outlet arrangement as shown in FIG. 8 and the passage arrangement as shown in FIG. 9.

(40) Pocket-shaped recesses 45 are provided on the inner surfaces of the housing 2, in particular in the connecting sockets 28 associated to the passage openings 3, 4, 5. The recesses 45 each interact with a corresponding freeform surface 46 in the passage duct 8 of the rotary part 6. The pocket-shaped recesses 45 in the housing 2 are non-symmetrical in relation to a longitudinal center plane 50 spanned by the axes 36, 52 of the passage openings 3, 4, 5. The longitudinal center plane 50 corresponds to the drawing plane as shown in FIGS. 8 and 9. In particular in the outlet arrangement shown in FIG. 8 but also in the passage arrangement shown in FIG. 9, a transition to the passage duct is free of edges, in other words free of joints. A geometric joint is avoided by adapting the contours in the connecting sockets 28 and in the passage duct 8. Further details concerning the joint-free design can be found in DE 39 22 240 C2.

(41) The housing cover 14 is screwed to the housing main body 21 using several fastening screws 26. The housing cover 14 is sealed against the housing main body 21 by means of a circumferential annular seal 27. The annular seal 27 is a housing cover seal. The annular seal 27 is freely accessible from an interior of the housing 2 of the diverter valve 1. The annular seal 27 is configured to come into contact with product. The annular seal 27 enables wet cleaning of the housing 2 without having to open the housing 2 in order to do so. The diverter valve 1 can be cleaned in a closed condition using a liquid. The diverter valve 1 allows liquid cleaning to be carried out to comply with Cleaning-in-Place hygiene requirements.

(42) The outer contour 9 of the rotary part 6 is designed with the cone angle κ in relation to the axis of rotation 7. In the exemplary embodiment shown, the cone angle κ is 20°. It is advantageous if the cone angle κ is between 50° and 80°, in particular between 10° and 40°, in particular between 15° and 25°.

(43) The passage openings 3, 4, 5 are each provided with connecting sockets 28 formed in one piece with the housing main body 21, the connecting sockets 28 allowing a simpler and improved connection of conveyor lines to the housing 2. In an advantageous embodiment, a pipe socket 29 sealed by means of a flange seal 30 coming in contact with the product can be flanged to each of the connecting sockets 28. The pipe sockets 29 provide a standardized connection interface to integrate the diverter valve 1 into a conveyor system. The pipe sockets can easily be screwed to the housing. This allows the diverter valve 1 to be adapted to the required pipe-cross-section of a conveyor system by a suitable selection of the pipe sockets 29. The diverter valve 1 can be integrated into an existing conveyor system in a flexible and uncomplicated manner.

(44) The function of the diverter valve 1 comprising a gap seal will be explained in more detail in the following sections:

(45) In order to convey a material to be conveyed along the passage direction 42 or the outlet direction 41, the rotary part 6 is first arranged in the housing 2 in a sealed manner. In order to arrange the rotary part 6 in the housing 2 in a sealed manner, the rotary part 6 is pressed, by means of the axial drive 15, into the housing 2 along the axis of rotation 7 until the rotary part 6 is arranged in the housing 2 with a defined radial gap between the outer contour 9 and the inner contour 17. The radial gap is in particular between 0.01 mm and 0.5 mm, in particular between 0.02 mm and 0.3 mm, in particular between 0.03 mm and 0.2 mm, and in particular between 0.05 mm and 0.1 mm.

(46) In this arrangement, the rotary part 6 is sealed in the housing 2 by means of the cone sealing members 16. The rotary part 6 is in a conveying position, which is also referred to as conveying arrangement. Conveying material through the passage openings 3, 5 or 4, 5 connected to one another along the passage duct 8 can be carried out in a sealed manner. In order to change the material conveying path from the passage direction 42 to the outlet direction 41 or vice versa, the rotary part 6 is rotated about the axis of rotation 7 by means of the rotary drive 23. Rotating the rotary part 6 and the axis of rotation 7 can take place in the housing 2 in the conveying arrangement of the rotary part 6. In the sealed arrangement, the rotary part 6 is rotatable about the axis of rotation 7 in the housing 2. In order to facilitate the rotation of the rotary part 6, the rotary part 6 can be pulled out of the sealed arrangement along the axis of rotation 7 in the housing 2, in other words it can be displaced towards the axial drive 15, prior to the rotary movement.

(47) In order to clean the diverter valve 1, the passage duct 8 is in particular rinsed first in the passage direction 42 and in the outlet direction 41 via the conveyor lines connected to the diverter valve 1, with the rotary part 6 in particular remaining in the conveying position. The rotary part 6 is then displaced axially along the axis of rotation 7 in the housing 2 towards the housing cover 14. The rinsing arrangement of the diverter valve 1 is shown in FIG. 11. For this purpose, the housing 2 has a clearance 44 into which the rotary part 6 can be moved with its larger front end face 10. The housing 2 remains closed during the axial displacement of the rotary part 6. It is not necessary to open the housing 2 in order to clean the diverter valve 1, in particular to rinse the rotary part 6 and the inner surfaces of the housing main body 20 and of the housing cover 14.

(48) This axial displacement increases the radial gap between the outer contour 9 and the inner contour 17. In the cleaning arrangement or rinsing arrangement of the diverter valve 1 as shown in FIG. 11, the cleaning gap 31 has a size of approximately 1.5 mm to 2.0 mm. It is advantageous if the cleaning gap 31 has a size of 0.5 mm to 4 mm, in particular between 1.0 mm and 3.0 mm.

(49) The cleaning gap 31 is also referred to as rinsing gap. The cleaning gap 31 ensures that cleaning liquid, which is fed into the housing 2 via the passage openings 3, 4, 5, for example, is also able to reach the surface sections of the outer contour 9 of the rotary part 6, the inner contour 17 of the housing 2 and the inner surface of the housing cover 14. The entire interior of the housing 2, in particular the gap between the outer contour 9 and the inner contour 17, can be rinsed with cleaning liquid. The cleaning arrangement shown in FIG. 11 is also referred to as rinsing arrangement, allowing depositions and inadvertent accumulations of dirt to be removed from the diverter valve 1.

(50) FIG. 11 shows the diverter valve 1 in a mounting position in which the housing cover 14 is oriented vertically. In the arrangement shown in FIG. 11, the passage direction 42 is oriented horizontally. The outlet direction 41 is directed diagonally downwards. The conveying plane is oriented vertically. This arrangement is shown schematically in FIG. 2.

(51) Basically, a mounting position with horizontal passage direction 42 and an outlet direction 41 directed diagonally upwards as shown in FIG. 3 is also conceivable. In this arrangement, the conveying plane is oriented vertically as well. Correspondingly, the housing cover 14 is oriented vertically.

(52) A mounting situation in which the passage direction 42 is oriented vertically with an outlet direction 41 directed diagonally upwards (cf. FIG. 4) or diagonally downwards (cf. FIG. 5) is also conceivable. In both cases, the conveying plane is oriented vertically. In both cases, the housing cover 14 is oriented vertically. The mounting positions described previously are the preferred mounting positions for the diverter valve. In these mounting positions, only a small amount of rinsing liquid remains in the system. These mounting positions are preferred.

(53) The diverter valve can also be used when the housing cover 14 is oriented horizontally. It is advantageous if the housing cover 14 is arranged on the upper side of the housing 2 in a horizontal mounting position. Removing the rotary part 6, in particular for maintenance and/or cleaning, is simplified. An arrangement in which the housing cover 14 is oriented horizontally and arranged on the lower side of the housing 2 is generally also conceivable. Here, a greater amount of rinsing liquid remains in the diverter valve. These two mounting positions require a longer and more intensive drying of the diverter valve.

(54) In the example of the diverter valve according to the invention, the mounting position and the type of seal used for the rotary part 6 in the housing 2 are independent of each other. Every possible type of seal for sealing the rotary part relative to the housing can be used in any mounting position.

(55) The design and function of the diverter valve 1 with a seal provided on the passage duct 8 will be explained in more detail in the following sections with reference to FIGS. 12 to 14.

(56) In this further embodiment of the diverter valve 1, the essentially annular openings of the passage duct 8 on the rotary part 34 each have a circumferential passage duct sealing member 35. The passage duct sealing members 35 are arranged circumferentially in relation to the passage duct longitudinal axis 36 on the outer contour 9 of the rotary part 34. Apart from that, the arrangement, and in particular the positioning of the rotary part 34 in the housing 2, remain essentially unchanged. An essential difference with respect to the previous embodiment is that the sealing gap between the outer contour 9 of the rotary part 34 and the inner contour 17 of the housing 2 is increased. The radial gap is in particular between 0.1 mm and 2.0 mm, in particular between 0.2 mm and 2.0 mm, in particular between 0.3 mm and 1.2 mm, and in particular between 0.4 mm and 0.8 mm. It is advantageous if the radial gap between the conical outer contour 9 of the rotary part 34 and the inner contour 17 of the housing 2 is designed with a gap space that is as small as possible. In order to ensure rotation of the rotary part 34, the rotary part 34 can be pulled out of the housing 2 axially along the longitudinal axis 7 at least along sections thereof. It is preferred if the rotary part 34 is rotated in the housing with a narrow radial gap.

(57) As in the previous embodiment of the gap seal, the rotary part 34 with the passage duct sealing members 35 is arranged rotatably in the housing 2. It is not necessary to displace the rotary part 34 axially in the housing to ensure rotatability of the rotary part 34 about the rotary axis 7.

(58) A special feature of the design of the passage duct sealing member 35 is that the circumferential sealing groove 37 is essentially dovetailed, in other words the groove width b increases with increasing groove depth t. In the depth direction, the groove width b increases initially in a width direction, with the result that the passage duct sealing member 35 is held reliably in the groove 37. In particular, the groove width in the region of the surface 38 of the rotary part 34 is smaller than the width of the passage duct sealing member 35 in an original condition. The passage duct sealing member 35 is biased in the groove 37 on the surface 38 and is clamped in the groove width direction.

(59) To improve the retention of the passage duct sealing member 35 in the groove 37, the width of the passage duct sealing member may also increase with increasing groove depth t. The contour of the section of the passage duct sealing member 35 arranged in the groove 37 is essentially also dovetailed, with the width increasing at least in particular in one direction. In particular, the contour of the section of the passage duct sealing member 35 arranged in the groove 37 is essentially identical to the groove cross-section. The maximum width of the passage duct sealing member 35 is in particular greater than that of the surface 38 of the opening of the groove 37 facing the rotary part 34. The passage duct sealing member is made of an elastomer material.

(60) According to the exemplary embodiment shown, the passage duct sealing member 35 protrudes from the groove 37 on the surface 38 of the rotary part 34. This improves a sealing effect of the passage duct sealing member 35. According to the exemplary embodiment shown, the protrusion D relative to the surface 38 is in particular between 0.5 mm and 1.0 mm. The cross-sectional shape of the passage duct sealing member 35 is essentially rectangular, with the protruding section of the passage duct sealing member 35 protruding from the groove 37 having lateral transition chamfers 39. The transition chamfers 39 improve the sealing effect against the rotary part 34. The transition chamfers 39 enable a continuous transition from the surface 38 of the rotary part 34 to the surface 43 of the passage duct sealing member 35.

(61) In order to rinse the diverter valve 1 comprising passage duct sealing members 35, the rotary part 34 is axially displaced in the housing 2 as in the previous embodiment until the rinsing gap is obtained. As the passage duct sealing members 35 protrude from the outer contour 9 of the rotary part 34, the rinsing gap is—in this embodiment—defined as the distance between the inner contour 17 of the housing 2 and the passage duct sealing members 35. The rinsing gap defined in this manner is—in this embodiment—identical to the rinsing gap of the diverter valve 1 comprising a gap seal.

(62) The design and function of another embodiment of a diverter valve without radial gap will be explained in the following sections with reference to FIG. 15.

(63) In this embodiment of the diverter valve 1, the rotary part 40 is designed without sealing member according to the exemplary embodiment shown. A sealing of the rotary part 40 in the housing 2 is brought about in such a way that the rotary part 40 is in direct contact, with its conical outer contour 9, with the conical inner contour 17 of the housing 2, in other words the rotary part 40 is in full contact with the housing 2. In this arrangement, there is no radial gap or the radial gap is 0 mm. For this embodiment, it is advantageous if at least one of the surfaces resting against one another has a particular surface treatment and, in particular, has a surface refinement, in particular has a particular surface hardness. It is also possible to apply a hardening layer to the surfaces of both components, i.e. of the housing 2 and of the rotary part 40. It is advantageous if the surfaces have a hardening layer configured as a chromium layer. It is advantageous if only the surface of the rotary part 40 is designed with the chromium layer.

(64) It is conceivable to provide a cone sealing member 16 configured as an O-ring in addition to the full-contact arrangement on the outer contour of the rotary part 40.

(65) In order to rotate the diverter valve configured such that the rotary part 40 thereof is in full contact with the housing, it is necessary to remove the rotary part 40 from the housing 2. This can be done, for example, by a comparatively small axial displacement of a few tenths of a millimeter up to some millimeters. The slight axial displacement of the rotary part 40 can be carried out when the pneumatic lifting drive, i.e. the axial drive 15 is depressurized. By means of a plate spring not shown, which is mounted in a biased condition, the rotary part 40 is lifted off the conical internal contour 17 of the housing 2.

(66) In the lifted-off arrangement of the rotary part 40, said rotary part 40 can be rotated for example between the passage arrangement and the outlet arrangement.

(67) In this arrangement, the rotary part 40 can, however, also be rotated about the axis of rotation 7 to scrape off and discharge product that has deposited there. In order to perform the actual rinsing, the rotary part 40 is pulled out of the housing 2 further along the axis of rotation 7 until a larger, defined rinsing gap is formed.

(68) Another axial displacement is performed by the axial drive 15, by activating, i.e. operating the latter.

(69) Instead of the biased plate spring, it is also possible to use an axial drive 15 configured as two pneumatic cylinders connected in series.

(70) Axially displacing the rotary part 40 can also take place in a single stage, a relief member for depressurizing the axial drive 15 in particular being omitted. Rotating and cleaning the rotary part 40 is then performed in a condition of maximum axial displacement, i.e. in the rinsing arrangement.

(71) The function, in particular the rinsing of a diverter valve will be explained in more detail in the following sections with reference to FIG. 16. As shown in FIG. 16, the rotary part 40 is in the axially displaced condition. Additionally, the rotary part 40 has been rotated about the longitudinal axis 7, in other words it is neither in the passage arrangement nor in the outlet arrangement but in a rinsing rotary position in which the passage duct 8 faces none of the passage openings 3, 4, 5. In particular, the greatest part of the first passage opening 3 and the pipe section connected thereto are blocked by the rotary part 40. Rinsing water, which is pressed into the lateral cover area through the gaps between rotary part and housing, flows through said lateral cover area intensively. The rinsing water is then flushed, via additional gaps, into one of the discharging pipe sections connected to the passage openings 4 and/or 5. It is advantageous that the rotary drive 23 of the diverter valve 1 enables the rinsing position of the rotary part 40 with a third central position.

(72) When the position of the rotary part is changed during rinsing, the cleaning liquid is flushed into all areas of the housing, thus allowing all accumulations of dirt or old product to be removed.

(73) In order to dry the diverter valve, in particular the rotary part 40, the rotary drive 23 can be moved into the central position shown in FIG. 16. In order to accelerate the drying process, the rotary part can also be moved axially to generate a sufficiently turbulent flow, and in particular to dry all areas of the diverter valve 1 and of the rotary part 40 safely and to remove larger amounts of rinsing water from potential dead zones. The air speed in the diverter valve must be selected such that water is blown off. This air speed is between 15 m/s and 40 m/s, preferably between 25 m/s and 30 m/s, in the pipeline. Correspondingly higher air speeds will then develop in the gaps, allowing any water that has accumulated there to be carried away safely for a fast drying result.

(74) It is conceivable for the housing bottom 20 to be designed in a planar manner. It is conceivable for a collecting trough to be integrated in the housing bottom 20, which—as shown in the sectional view of FIG. 15—has a essentially v- or u-shaped design. The shape of the housing bottom 20 depends in particular on the mounting position of the diverter valve 1.

(75) Another embodiment of a diverter valve will be explained in the following sections with reference to FIGS. 17 and 18.

(76) The rotary part 56 essentially corresponds to the rotary part 40 of the previous embodiment, with an additional breakthrough 57 being provided. The breakthrough 57 is essentially cylindrical and has chamfers 58 on the transitions facing the front end faces 10, 11 of the rotary part 56. The breakthrough 57 has a breakthrough longitudinal axis 59, which is oriented parallel to the longitudinal axis 7 of the diverter valve 53. The breakthrough 57 reduces the mass of the rotary part. Also, it improves the rinsing of the diverter valve 53, in particular in the area of the lateral surfaces. What is essential is that the breakthrough 57 extends from at least one of the front end faces 10, 11 of the rotary part 56. It is also conceivable to provide a recess configured in the manner of a blind hole instead of the breakthrough, said blind hole extending along the breakthrough longitudinal axis 59 without penetrating the entire rotary part 56.

(77) The breakthrough longitudinal axis 59 can be arranged at an angle of inclination relative to the longitudinal axis 7. This angle of inclination can amount to up to 20°.

(78) The breakthrough longitudinal axis 59 is oriented in particular perpendicular to the passage duct longitudinal axis 36. The passage duct longitudinal axis 36 and the breakthrough longitudinal axis 59 are oriented in a screw configuration such that the passage duct 8 and the breakthrough 57 run separately from one another in the rotary part 56. The breakthrough 57 is integrated in the rotary part 56 at a distance from the passage duct 8. The passage duct 8 and the breakthrough are not connected to one another. The breakthrough 57 is a relief bore.

(79) When cleaning the diverter valve 53 using a liquid, the breakthrough 57 improves the cleaning result. As soon as liquid, in particular water, escapes through one of the lateral discharge openings of the breakthrough 57, the front ends of the rotary part 56 are flushed more intensively.

(80) Another embodiment of a rotary part 60 will be explained in the following sections with reference to FIG. 19. The rotary part 60 essentially corresponds to the rotary part 56, with the breakthrough 57 being formed in the manner of an elongate hole along a circular arc. The opening angle α of the circular arc in relation to the longitudinal axis 7 is 90° in the exemplary embodiment shown. The opening angle α may also be greater than 90° or smaller than 90°. The width B of the elongate hole is half the radius of the smaller front end face 11 in the exemplary embodiment shown. The width B of the elongate hole can also be selected greater or smaller. It is advantageous if the breakthrough 57 is as large as possible to reduce the mass of the rotary part 60 to the greatest possible extent. When designing the breakthrough 57, great care must be taken to ensure that the breakthrough 57 and the passage duct 8 do not intersect one another. The stability and rigidity of the rotary part 60 is ensured despite the breakthrough 57.

(81) Another embodiment of a rotary part 61 will be explained in the following sections with reference to FIG. 20.

(82) The rotary part 61 essentially corresponds to the rotary part 56 of the previous exemplary embodiment. The most important difference is that the breakthrough 57 has a double-conical design. Starting from the openings arranged respectively at the front end faces 10, 11, the breakthrough 57 tapers at a breakthrough cone angle ω. In the exemplary embodiment shown, the breakthrough cone angle ω is 1°. The breakthrough cone angle ω can however also be selected greater or smaller than 1°. It is advantageous if the breakthrough cone angle ω in the breakthrough 57 facilitates an automatic outflow of cleaning liquid from the breakthrough towards the front end faces 10, 11.

(83) The double-conical design of the breakthrough 57 is symmetrical. This means that the cone sections of the breakthrough 57 meet in the longitudinal center plane 50 in which the passage duct longitudinal axis 36 is disposed as well. In particular, the two breakthrough cone angles co of the cone sections of the breakthrough 57 are identical. It is also conceivable that the depths of the cone sections of the breakthrough 57 are different from one another such as to meet in particular outside the longitudinal center plane 50. The breakthrough cone angles co can also be defined differently.

(84) Another embodiment of a rotary part 62 will be explained in the following sections with reference to FIGS. 21 to 23. The most important difference with respect to the previous embodiments is that the outer contour 9 of the rotary part 62 is not conical over the entire circumference. The outer contour extends across an opening angle γ relative to the longitudinal axis 7, the opening angle γ being greater than 180°. In the exemplary embodiment shown, the opening angle γ is 200°.

(85) The rotary part 62 corresponds to a segment of a cone. The outside 63 of the rotary part 62, which is not visible in FIG. 21, is planar. The surface opposing the outside 63 is straightened in sections. The straightened section 64 is parallel to the outside 63.

(86) Another embodiment of a diverter valve will be explained in the following sections with reference to FIGS. 24 to 26.

(87) The passage duct sealing member 35 of the diverter valve 1 is essentially configured as an O-ring, which is arranged in a corresponding sealing groove 37. The cross-sectional shape of the passage duct sealing member 35 and the contour of the sealing groove 7 correspond to one another, with the result that the sealing groove 37 is completely filled by the passage duct sealing member 35. Dead zones are avoided.

(88) The passage duct sealing member 35 has a protruding section, which comprises two transition chamfers 39 that meet in an essentially linear surface 43. The linear surface 43 forms a contact edge of the passage duct sealing member 35 on the inner contour 17 of the housing 2.

(89) Another embodiment of the passage duct sealing member will be explained in the following with reference to FIG. 27. Just like the embodiment of FIG. 26, the passage duct sealing member 65 is designed essentially in the manner of an O-ring. The only difference is that the protruding section has transition curvatures 66 instead of the transition chamfers, the transition curvatures 66 providing a transition to an essentially planar surface 43. The contact surface between the surface 43 of the passage duct sealing member 65 and the inner contour 17 of the housing 2 is thus increased.