Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
  • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
  • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
  • F16K3/16—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together
  • F16K3/18—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members
  • F16K3/184—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members by means of cams
  • F16K3/186—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members by means of cams by means of cams of wedge from
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K25/00—Details relating to contact between valve members and seat
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
  • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
  • F16K3/16—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together
  • F16K3/18—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members

Definitions

• the invention relates to a double plate slide for piping, in particular a double plate slide with wedge-in-wedge principle for the sealing washers and a pipe bridge.
• a tubular passage ensures almost unimpeded flow of the medium, which is passed through the tube to be shut off.
• This pipe bridge has seals or sealing surfaces which cooperate with sealing units on the housing of the double plate slide.
• two sealing discs ensure the tight closure of the two tube ends, between which the double plate slide is arranged.
• the double plate gate valve is used in particular in technical plants of the chemical industry.
• a wedge disposed at one end of an actuating rod is moved into another wedge to urge the two sealing disks in the closed position of the double gate valve against gaskets which enclose the housing space of the obturator against the ingress of gas or contaminants to seal.
• the double plate slide has a slide housing with two pipe sockets and two housing sealing seats, between which a sealing plate consisting of two shut-off plates with sealing rings is displaceable.
• the horizontal mounting position of the gate valve is shown in a vertical tube, wherein the pipe bridge is arranged adjacent to the sealing plate, on the opposite side of the actuating rod.
• the pipe bridge can also be arranged below the sealing plate, this is the case when the gate valve is installed vertically, in a horizontal pipe.
• the pipe bridge has the disadvantage that it is composed of two sealing rings and a compensator connecting the sealing rings to one another.
• the compensator consists of an inner tube section and a coaxially extending outer tube section, wherein the outer tube section is fixedly connected to both sealing rings, namely welded and has a circumferentially extending shaft or indentation.
• the inner tube section is hollow-cylindrical, so that no flow losses caused thereby occur.
• the inner tube section is firmly connected only with one of the two sealing rings.
• Compared to the other sealing ring of the inner tube section is axially movable, wherein the axial clearance between the sealing ring and the inner tube section is between 1.0 mm to about 5.0 mm.
• the interior surface of the inner pipe section is aligned with the inner surfaces of the sealing rings, so that a virtually continuous flow passage is created in the open position of the slider.
• the circumferential recess of the outer pipe section extends to near the outer surface of the inner pipe section, so that the pressure prevailing in the housing interior gas pressure on the circumferential recess on the sealing rings under axial spread of the same is fully effective.
• the axial spreading of the sealing rings is possible on the one hand by the circumferential indentation and on the other hand by the axial clearance between the inner pipe section and one of the two sealing rings.
• the pipe bridge is therefore limited by the two sealing rings on the one hand and the arranged between them, serving as a compensator inner and outer pipe sections on the other hand to form a ring box.
• This ring box or annulus between the inner and outer tube section is filled with a heat-insulating material such as glass wool or rock wool, with the additional purpose of preventing the ingress of flow medium in said annulus. Clogging of the annulus with flow medium or gas flow with dust and dirt particles or similar deposits would, after prolonged use, interfere with the action of the compensator.
• a double plate valve for pipes comprising a pipe bridge which is inserted in the open position of the slide in the pipeline and comprises a circumferential pipe section, at the front ends of which sealing rings are arranged, in the open position of the slide under elastic bias can be pressed against sealing seats of the valve body, and wherein at least one end face of the pipe section is mounted axially displaceable at least relative to one of the sealing rings.
• the pipe section has at a front end to a bearing ring in which a circumferential receiving groove is formed, in which a circumferential ring member is axially displaceably and resiliently supported with a circumferential projection to the adjacent sealing seat.
• a circumferential ring element with a projection forms part of the pipe bridge and is designed to be heat-resistant for this purpose.
• the projection engages in a receiving groove of a bearing ring.
• the circumferential ring element is therefore designed such that it forms part of the inner wall of the pipe bridge, whereby the pipe bridge can be used for both flow directions.
• the object of the invention is to provide a double plate slide, is largely prevented in the case that dirt gets into the valve body when the double plate valve is installed in a horizontal line.
• the translatory actuating element is connected to a system carrier plate, which transmits the adjusting movement of the actuating element in the direction of the open position and in the closed position to the first and second sealing plate.
• the system carrier plate has in this case in its region facing the drive a recess for the passage of the pipe bridge.
• the system carrier plate transmits the adjusting movement in the closed position to the first and second sealing plate in a form-fitting manner and also in the direction of the open position in a form-fitting manner.
• the positive connection in the closed position has in the direction of the open position a frictional connection, which allows for a small stroke an adjusting movement of the system carrier plate, without this hub is transmitted to the sealing plates.
• the positive-locking connection which is effective in the direction of the open position, has sufficient play in the direction of the closed position for an idle stroke of the system carrier plate relative to the sealing plates.
• the system carrier plate extends in the longitudinal direction over about 2/3 of the length of the housing and is approximately as wide in width as the housing interior.
• the maximum width is selected so that guides for the system carrier plate and / or the sealing plates can be provided along the inner wall of the housing.
• the first sealing plate on its side facing the second sealing plate along the two longitudinal sides of a plurality of bushings and has the second sealing plate on its first sealing plate side facing along the two longitudinal edges with the bushing corresponding bolts, which with axial play and are inserted into each other with radial play and are connected to each other by means of a positive connection.
• both sealing plates are aligned with each other during assembly.
• the free end of the bolt is formed as a mandrel, on which a compression spring is arranged. Due to the distance to the pipe bridge, the thermal influence on the mechanical restoring force of the spring is as small as possible.
• a bushing and a corresponding bolt each form a connecting element which keeps the two sealing plates at a distance from each other, wherein the distance varies slightly, since the two sealing plates can easily be spread apart in order to be as tight as possible against the inside of the housing come. Overall, the spreading force acts at several points, so that angling of the sealing plates to each other is avoided.
• the system support plate extends in the longitudinal direction over about 2/3 of the length of the housing and is approximately as wide in width as the housing interior. This is the maximum possible length, since the system support plate should be able to assume an upper position where it strikes the top of the housing, in which the pipe is locked, and to be able to assume a lower position in which the pipeline is released.
• the maximum width is selected so that guides for the system carrier plate can be provided along the wall of the housing.
• two carrier systems are arranged on the lower edge of the system carrier plate, which are firmly connected to the system carrier plate and engage behind the individual sealing plate or the first sealing plate and the second sealing plate in a form-fitting manner.
• the fixed connection of the carrier systems with the system carrier plate can take place via a frictional connection.
• a movement of the system carrier plate in the closed position is transmitted via the positive connection of the carrier systems on the sealing plates, which are thereby pressed against the upper stops.
• the carrier systems initially release the two sealing plates.
• the carrier system comprises a sleeve, in which the bolt of a clevis pin connection is arranged, wherein the bolt at the end facing away from the clevis has a thread for receiving a nut and in the sleeve on the bolt a spring assembly is arranged and the clevis is firmly connected to the system support plate, and two support plates on the sleeve portions between the first and second sealing plate and partially over the two sealing plates survive, in this projecting portion, the thickness of the support plates is greater than the distance of the first sealing plate to the second sealing plate.
• the spring assembly is claimed to train when the sealing plates arrive in the process in the closed position at its upper stop and the system support plate but is moved further upwards.
• the sealing plates When the sealing plates have reached their upper stop, the sealing plates are aligned with the openings of the pipeline to be shut off. Only with the other system carrier plate, the wedge-in-wedge effect is activated by a wedge assembly is pulled on the system carrier plate in the arranged on the rear sides of the sealing discs wedge seats.
• the system carrier plates on their longitudinal sides on two recesses for performing the connecting elements of the first sealing plate and the second sealing plate, wherein the upper end of the recess during the process in the open position, the movement of the driven system support plate form-fitting manner on the connecting element and thus transfers to the first sealing plate and the second sealing plate.
• the recesses are sized in length so that the lower edge of the recess is spaced from the connecting element, so that during the movement of the system support plate in the closed position, this is not connected to the gleichsele- not even if they are already stationary, because the sealing plates have arrived at their upper stop.
• a wedge is arranged centrally on each of the first sealing disk and the second sealing disk on the respectively mutually facing sides, wherein the two rear wedges form a wedge seat and the drive indirectly pulls a wedge arrangement into the wedge seats.
• the longitudinal movement of the driven system support plate is converted into a transverse movement of the sealing disks in the direction of the sealing surfaces on the housing or on the nozzle.
• the system support plate in its lower edge in the middle on a in the direction of the center of the sealing washers and beyond extending recess in which a slider is guided with recessed in a circular recess ball, wherein upon movement of the system support plate in the direction Closed position of the slider via a ball mechanism two wedges with moves in the vertical direction, both wedges act with their respective inclined plane on the inclined planes of the wedge seats on the sealing discs such that the sealing discs perform a horizontal movement and press against the sealing surfaces in the nozzle ,
• the pipe bridge consists of two pipe halves, wherein the first Rohrhote is attached to the first sealing plate and the second half tube is attached to the second sealing plate and the first half tube has a circumferential groove for receiving a circumferential projection of the second Rohrhote.
• a radial sealing ring is arranged between the two tube halves in order to reduce the penetration of dirt from the medium flowing through into the housing.
• peripheral projection may have a flat gasket on the face side, which should likewise avoid soiling of the housing interior.
• a housing purging can be provided, with the housing upper part and the housing lower part preferably having flushing connections.
• the purge pressure in the housing is greater than the medium pressure in the line. If the sealing plates have moved up against the stop, a gap remains between the sealing plates and the sealing system of the housing or the nozzle. Through this gap, the flushing medium with high speed flow and eliminate any impurities on the mutual sealing surfaces until the system support plate has completely pulled the wedge mechanism in the wedge seat.
• the process in the closed position is switched off when a previously defined torque of the drive is reached.
• the still existing flushing pressure supports the pressing of the sealing plates to the housing-side sealing surfaces. Should one of the two sealing rings be damaged, the medium from the pipeline would still not get into the housing of the double plate slide due to the higher pressure of the flushing medium.
• the dense gap between the housing sealing rings and the surfaces of the sealing plates may be provided with a minimum defined permeability, so that the sealing surfaces are permanently purged and thus not pollute.
• the double plate slide according to the invention can also be installed horizontally in a vertical line. In this installation position, a guide for the sealing plates and the system support plate may be provided.
• Figure 1 shows, as a portion, a housing of a double plate pusher
• Figure 2 shows a section along A-B of the double-plate gate valve of Figure 1;
• FIG. 3 shows in detail the sealing system
• Figure 4 is a partial view of Figure 2 and the connection of the left sealing disc with the left sealing plate;
• Figure 5 shows a detail of Figure 2 is a plan view of the connecting element of the first sealing plate with the second sealing plate;
• Figure 6 is an illustration in section through the connecting element of Figure 5;
• Figure 7 shows a detail view of Figure 2 shows a section through the pipe bridge
• FIG. 8 shows a detail of Figure 2 shows the carrier system; and FIG. 9 shows the upper housing part with the lantern.
• FIG. 1 shows, as a section, a housing of a double-plate slide in which a pipe bridge and two sealing plates are displaceably arranged.
• the housing In the left half of the drawing, the housing is shown in a plan view, in the right half of the drawing in a section through the median plane.
• a system support plate 1 In the elongated housing of the double plate slide a system support plate 1 is slidably disposed, whose width is slightly less than the inner width of the housing and whose length is about 2/3 of the length of the housing.
• the system carrier plate 1 is connected to an actuating element 2 such as an actuating rod or a spindle.
• the system support plate 1 In the upper region, the system support plate 1 has a cutout 3 for the passage of a pipe bridge 4.
• the upper half of the cutout 3 is circular, wherein the radius is only slightly larger than half of the outer diameter of the pipe bridge 4.
• the lower half of the cutout 3 has a defined larger radius than half of the outer diameter of the pipe bridge 4.
• On both sides of the System support plate 1 are approximately centrally cutouts 5 for performing connecting elements 6 for connecting a first sealing plate 7 with a second sealing plate 8.
• the cutouts 5 are formed as in the longitudinal direction of the system support plate 1 extending slots.
• the system support plate 1 has centrally a section 9 extending towards its center, in which an actuating element 10 for the wedge-in-wedge principle is arranged.
• At the lower end of the system support plate 1 are further eccentrically two support systems 11 for the first and the second sealing plate 7, 8 attached.
• the first sealing plate 7 is above the system support plate 1 and the second sealing plate 8 below the system support plate 1.
• the two sealing plates 7, 8 are connected via connecting elements 6 with slight play and kept at a distance.
• Each of the two support systems 11 is frictionally connected to the system support plate 1 and engages behind the two sealing plates 7, 8 such that vertical movement of the system support plate 1 upwards over a positive connection of the carrier systems 11 is transmitted to the sealing plates 7, 8, which are thereby also moved upwards.
• a vertical movement of the system support plate 1 down is transmitted to the disk tray 12 that the upper ends of the cutouts 5 press in the system support plate 1 against the connecting elements 6.
• the case of a double plate slide shown here consists of three sections.
• the three-part housing consists of an upper housing part 13, a middle part 14 and a lower housing part 15.
• the upper housing part 13 is provided with a lantern not shown here for receiving a drive, wherein the drive can be made electrically, hydraulically or pneumatically.
• the driven actuator 2 and the spindle the movement of the accommodated in the housing disk tray 13 is realized with integrated system support plate 1.
• flushing lines 16 can be arranged with flanges 17 for a flushing system.
• In the interior of the upper housing part 13 are also stops 18, against which the plate basket 12 is driven upon reaching the closed slide position.
• the stops 18 block the sealing unit, so the sealing plates 7, 8 with the sealing discs 23, 24, at the end of the closing stroke.
• a spring clutch in the carrier system 11 allows an additional travel of the system carrier plate 1 to allow the engagement of a wedge unit and the construction of a wedge force, whereby the bias for the sealing system is supplied, as will be explained in connection with Figure 8.
• the housing middle part 14 On the housing middle part 14 are flanges for mounting the double plate slide in a pipeline. Inside the housing are the receptacles for a replaceable sealing system, which consists of materials that meet the operating conditions. Furthermore, the flanges 19, 20 for the connection to the upper housing part 13 and the lower housing part 15 are located on the middle part of the housing. Purge connections with corresponding flange connections can be realized on the middle part 14 of the housing.
• the housing middle part 14 may be made of a different material than the upper housing part 13 and the lower housing part 15. Since the middle part 14 has the nozzle for the pipe, it may be made of high quality material that is particularly resistant to heat or mechanical stress.
• the lower housing part 15 can be provided with flushing pipes with corresponding flange connections. Also, cleaning openings can be provided, through which then penetrated dirt can be removed. Due to the three-part embodiment of the housing is achieved in comparison to the prior art, which has a continuous housing with cover and bottom, a separation that makes the middle part 14 stiffer and enables it to accommodate higher forces. This division into three parts also makes it possible to realize the middle part 14 of a different material than the upper housing part 13 and the lower housing part 15 and thereby the dependence of the pressure, the temperature and the temperature distribution within the housing, of the process medium and the flushing medium to take into account.
• Another advantage of the three-part housing is that the wall thicknesses and Verrip- purged in particular the upper housing part 13 and the lower housing part 15 are not so expensive to perform as in a one-piece housing.
• the reason for this lies in the connecting flanges on the housing middle part 14, which can absorb higher forces.
• the elastic deformation under the operating loads including the piping forces are distributed more evenly in the three-part housing. It comes to lower stress and deformation peaks compared to a one-piece housing.
• Figure 2 shows a section along A-B of the double plate slide according to Figure 1.
• the system support plate 1 is moved over the driven actuator 2 in its uppermost position.
• the first sealing plate 7 and the second sealing plate 8 are moved against the stop 18.
• Two resting on the system support plate 1 wedges 21 have been pulled into wedge seats 22.
• Both wedge seats 22 are each firmly connected to the inside of a sealing washer 23, 24.
• the wedge force is applied to the sealing discs 23, 24 acting outwards.
• the two sealing disks 23, 24 are pressed against the housing-side sealing rings or sealing rings on the flanges for the pipe connection.
• the contact pressure via the wedge-Keilsitz- arrangement.
• Figure 3 shows the example of the right in the drawing sealing washer 23 as a detail of the sealing system consisting of the sealing ring 28 and an additional sealing element 29.
• On the housing is located in the region of a pipe socket 26 on the inside of the housing a circumferential groove 27.
• the sealing system consisting of the sealing ring 28 and the additional sealing element 29 is inserted into this circumferential groove 27, wherein the sealing ring 28 almost completely fills the circumferential groove 27 in height, but in the return heat tigen region of the groove 27 leaves a gap 30.
• the additional sealing element 29 is arranged, which may for example consist of an O-ring or a flat gasket.
• the sealing system shown in Figure 3 in the housing or in the socket 26 has a ring of polytetrafluoroethylene as a sealing ring 28 and as an additional sealing element 29 in the gap 30 of the circumferential groove 29 behind the sealing ring 28 lying O-ring.
• This arrangement is referred to as a soft seal system and can be used at temperatures of up to 200 0 C. Not shown is an embodiment for temperatures of 200 ° C, are used for the compound seals.
• the sealing ring made of round wound metals, which have either graphite or a mineral fiber in the interstices, wherein the mineral fiber can also be wrapped with graphite.
• the additional sealing element located in the gap 30 is then a flat gasket.
• the carbide ring uses chromium carbide coated metal rings.
• the underlying additional sealing element is a high temperature resistant flat gasket.
• the sealing washer 23 is shown in the released position, as during the travel.
• the pipe socket 26 is attached to the housing middle part 14. It may have a hardened surface with a hardness of 2000 HV in order to minimize the friction with the sealing ring 28.
• Figure 4 shows the example of the left in the drawing gasket 24, the connection of the sealing discs 23, 24 with the sealing plates 7, 8 and is a tea view of Figure 2.
• the second sealing plate 8 has a circular cutout 31 for receiving the corresponding circular sealing disc 24th on.
• a collar 32 is formed on the sealing plate 8 on the side facing the interior, on which a researcherorkragender circumferential outer portion 33 of the sealing washer 24 comes to rest.
• An internal fastening ring 34 covers both the outer portion 32 of the sealing disc 24, and a groove 35 of the second sealing washer 24.
• the groove 35 is formed on the inner circumference of the sealing disc 24 circumferentially and dimensioned in depth so that the top of the mounted mounting ring 34 is aligned with the housing interior facing surface of the sealing washer 24.
• the circumferential fastening ring 34 is fixedly arranged on the sealing disc 24, for example, it is screwed to it.
• a plurality of springs 36 are arranged distributed over the circumference.
• the springs are axially parallel with the sealing disc 24 and are compressed when the wedge unit in the closing operation, the sealing disc 24 pushes outward.
• the springs 36 are compression springs that support the return of the sealing disc 24 when opening the slide. In the illustration, the sealing disc 24 shifts during pressing by the wedge to the left and when releasing the wedge by the force of the spring 36 back to its original position as shown.
• the return of the sealing disc 24 via the one or more springs 36 also ensures that the sealing discs 24 do not stick to the sealing system or that the sealing disc does not drag over the sealing ring 28 during the process of the plate basket.
• the circumferential fastening ring 34 distributed over the circumference of a plurality of the second sealing plate facing blind holes 37 for receiving a torsion spring as a spring 36.
• a screw can be screwed through a hole in the mounting ring in a blind hole with internal thread in the gasket 24.
• FIG. 5 shows, as a detail from FIG. 2, a plan view of the connecting element of the first sealing plate 7 with the second sealing plate 8.
• the first sealing plate 7 has sockets 38 on its longitudinal sides on both sides of the housing interior, in this exemplary embodiment three sockets on each longitudinal side. which can be screwed or welded.
• the bushings 38 are provided with two coaxially opposed slots or circular holes 39 whose axis is perpendicular to the axis of the bushing 38.
• On the second sealing plate 8 are each opposite to the bushes 38 of the first sealing plate 7 bolts 40, which may be welded or screwed. In diameter, the bolts 40 are chosen so that they can be inserted into the sockets 38 of the first sealing plate 7 with some radial play.
• FIG 6 is an illustration in section through the connecting element 6 of Figure 5.
• the front part of the bolt 40 is designed like a mandrel for receiving a spring assembly 41.
• the bolt 40 includes a bore 42 which communicates with the two slots 39 in the shell the socket 38 is aligned.
• the connection of the first sealing plate 7 with the second sealing plate 8 can be done by a pin 43 which is passed through the first slot 39, the bore 42 in the bolt 40 and the second slot 39.
• the arranged on the mandrel spring assembly 41 for example, a torsion spring, the first and the second sealing plate 7, 8 under a defined bias, which provides for the pressing of the sealing surfaces of the two sealing plates 7, 8 to the sealing ring 28 on the pipe socket 26, when yourself the double plate pusher is in the open position.
• the system carrier plate 1 is arranged between the two sealing plates 7, 8 and has cutouts or recesses for the passage of the connecting elements 6.
• three connecting elements 6 are arranged distributed along both longitudinal sides of the sealing plates 7, 8, so that a tilting or twisting of the two sealing plates to each other is avoided.
• FIG. 7 shows a detail view of FIG. 2 of a section through the pipe bridge 4.
• the pipe bridge consists of two pipe halves, the first pipe half 44 being fastened to the first sealing plate 7 and the second pipe half 45 being fastened to the second sealing plate 8 and the first pipe half 42 has a circumferential groove for receiving a circumferential projection of the second tube half 43.
• the first sealing plate 7 and the second sealing plate 8 have a congruent circular cutout and the shell inner surfaces of the first tube half 44 and the second tube half 45 are aligned with the circular cutouts.
• the two tube halves 44, 45 are plugged into each other.
• the two tube halves 44, 45 may be sealed with a radial sealing ring 46 against each other.
• the tube half 45 may be provided on the front side at its projection with a gasket 47 and be sealed with a defined bias.
• FIG. 8 shows a detailed detail from FIG. 2 of the carrier system 11.
• the carrier system 11 is fastened to the system carrier plate 1 with a fork head 48.
• a spring system 49 is arranged, with a pushed onto a clevis pin 50 compression spring such as a torsion spring, wherein the lower end of the clevis pin 50 has a thread with nut 51 for adjusting a bias of the spring system 49.
• the housing of the spring system 49 has in the illustration on the right and left each support plate 52.
• the support plate 52 is rectangular in longitudinal section, wherein about the upper third between the first sealing plate 7 and the second sealing plate 8 is located. The remainder of the support plate 52 projects beyond the sealing plates 7 and 8.
• the suspension plates 52 are larger in cross-section than the distance of the first and second sealing plates 7, 8 from each other.
• the support plates 52 engage behind the sealing plates 7, 8 for the travel in the closed position of the double plate slide. Shown is the situation that the driven system support plate moves upward and the sealing plates 7, 8 have come to the two upper stops 18 to the plant. In the course of the further Fahrens upwards remain on the sealing plates 7, 8 arranged connecting elements 6 are and the system support plate with the slot 5 moves for a closing further up.
• the spring system is stretched so that a mechanical bias is established, which ensures in the opening process that the sealing plates 7, 8 initially not move down, even if the system support plate 1 begins the process down.
• the mechanical bias of the spring system 49 pulls the sealing plates 7, 8 initially upward in the direction of the system support plate 1.
• the length of the slot 5 is dimensioned so that its upper edge only comes to rest on the connecting element 6, if in the process down the mechanical bias of the spring system 49 is largely used up. Only then move the system support plate 1 and the sealing plates 7, 8 synchronously further down in the direction of the open position. This residence time of the sealing plates 7, 8 is used so that the wedge system removes the pressure of the sealing discs 23, 24 already from the sealing rings 28 in the nozzle 26 in order to achieve the least possible friction losses.
• the two sealing discs 23 and 24 have on the side facing the respective other sealing disc wedge seats, wherein the wedge point points downward.
• the wedge system has two centrally mounted on a ball mechanism wedges, the tip of which points upward.
• the ball 53 of the ball mechanism lies in a circular recess of a rectangular, flat slide 54.
• the slider 54 is guided in the vertical section 9 in the illustration.
• the slider 54 is immovably connected with the interposition of further elements with the system support plate 1. If the movement in the direction of the closed position, the sealing plates 7, 8 are driven to their stops 18 in front of block and the system support plate 1 moves further up, is on the inclined planes of the wedges du wedges the vertical adjustment movement in a horizontal contact pressure of the sealing discs 23, 24 converted against the sealing rings 28.
• the slider 54 has a recess at its lower edge 55, which initially has a smaller diameter and widens at a distance from the lower edge.
• the bolt 57 In the recess of the head 56 of a bolt 57 is in positive engagement.
• the bolt 57 is guided by a sleeve 58 and has at its downwardly over the sleeve 58 projecting end a thread for a nut 59.
• the sleeve 58 is provided with two mounting plates 60, via which it is firmly connected to the system carrier plate 1.
• the mounting plates 60 are nearly U-shaped with downwardly facing opening. Within the opening of the head 56 of the bolt 57 is located.
• the vertical position of the ball 53 can be adjusted.
• the horizontal position is determined by the leadership of the recess 9.
• FIG. 9 shows the upper housing part 13 with a lantern 61, which is provided for receiving the drive, which can be designed electrically, hydraulically or pneumatically.
• the drive designed as a spindle actuator 2 for the movement of the integrated system support plate and thus accommodated in the housing plate basket is realized.

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=38608380

Family Applications (1)

Country Status (5)

Cited By (1)

Families Citing this family (4)

Citations (3)

Family Cites Families (2)

• 2006
  • 2006-11-10 DE DE102006053373A patent/DE102006053373B3/de not_active Expired - Fee Related
• 2007
  • 2007-10-23 KR KR1020097008772A patent/KR20090064595A/ko active IP Right Grant
  • 2007-10-23 WO PCT/DE2007/001891 patent/WO2008055465A1/de active Application Filing
  • 2007-10-23 CN CN2007800417380A patent/CN101535694B/zh not_active Expired - Fee Related
  • 2007-10-25 TW TW096140006A patent/TW200835878A/zh unknown

Patent Citations (3)

Also Published As

Similar Documents

Legal Events