WO2016120205A1 - Hydraulischer rotationsdämpfer - Google Patents
Hydraulischer rotationsdämpfer Download PDFInfo
- Publication number
- WO2016120205A1 WO2016120205A1 PCT/EP2016/051445 EP2016051445W WO2016120205A1 WO 2016120205 A1 WO2016120205 A1 WO 2016120205A1 EP 2016051445 W EP2016051445 W EP 2016051445W WO 2016120205 A1 WO2016120205 A1 WO 2016120205A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- section
- rotary
- rotary damper
- housing
- Prior art date
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Classifications
-
- A—HUMAN NECESSITIES
- A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
- A47K—SANITARY EQUIPMENT NOT OTHERWISE PROVIDED FOR; TOILET ACCESSORIES
- A47K13/00—Seats or covers for all kinds of closets
- A47K13/12—Hinges
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
- E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
- E05F3/12—Special devices controlling the circulation of the liquid, e.g. valve arrangement
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
- E05F3/14—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with fluid brakes of the rotary type
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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/145—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only rotary movement of the effective parts
Definitions
- the invention relates to a hydraulic rotary damper according to the preamble of claim 1.
- Such a damper is known for example from WO 201 1/050517 A1.
- the movement of a toilet seat or a toilet lid is attenuated when lowering.
- the lifting should be possible with relatively little effort.
- the damping should be carried out so that the lowering movement is relatively fast, but a hit of the
- the generic rotary damper have a housing in which a rotary piston is rotatably guided.
- the housing has two diametrically arranged webs, which project towards the outer circumference of a piston portion and define together with this two pressure chambers which are filled with pressure medium, for example a highly viscous liquid.
- the piston is designed in a corresponding manner with two radial projections which dip into the two pressure chambers and thus each share in two subspaces, which are connected via throttle cross-sections with each other.
- a check valve on the one hand and on the other hand a spring-biased friction element is provided in the radial projections, which slides on a backdrop of the housing and thus generates a dependent on the rotation angle damping force during the rotational movement.
- dampers in which a wing is guided on each radial projection to overcome the above-mentioned disadvantages, which releases in one direction an additional flow or damping cross-section and closes in the other direction.
- the wings are sealingly against the inner peripheral wall of the housing. This wing can also be designed so that it releases the flow cross-section dependent on the angle of rotation during a pivoting in one direction or closes.
- the invention has for its object to provide a rotary damper, in which the risk of damage is reduced.
- Patent claim 1 solved.
- the rotary damper according to the invention has a sleeve-shaped housing in which a rotary piston is rotatably guided.
- the housing has to the rotary piston projecting webs, which limit together with this pressure chambers.
- On the rotary piston radial projections are formed, which divide the pressure chambers in each case into two subspaces whose volume changes with the angle of rotation of the rotary piston.
- controllable throttle cross sections are formed between the subspaces, which allow an overflow of pressure medium from a decreasing subspace to the adjacent, increasing subspace.
- These controllable throttle cross-sections are designed such that they are larger in a direction of rotation of the rotary piston than in the opposite direction of rotation.
- These controllable throttle cross sections may be formed in addition to further connection channels or throttle cross sections.
- At least some of the throttle cross-sections of the rotary damper are designed such that their effective cross-section decreases or increases in a rotational direction abruptly.
- the term "leaky” is understood to mean a more or less abrupt change in cross-section, which occurs during a fraction of the usual pivoting of the piston / housing.
- wake turbulence which substantially reduces the internal pressure of the housing relative to an internal pressure present in a laminar flow, for example by one third, so that instead of a pressure of for example 100 bar only about 66 bar rest in the housing - a Overloading of the rotary damper can thus be prevented in a surprising manner in a very simple manner.
- the envelope in a turbulent flow which is applied by the rotary damper acting against the sinking of the toilet seat set torque is increased, so that a gentle placement of the toilet set is ensured on the ceramic.
- the throttle cross-section is preferably designed so that initially in a first angular range of the said direction of rotation is a laminar flow with a concomitant relatively low torque.
- the envelope into the turbulent flow of the pressure medium then takes place in that angle range in which, for example, the toilet seat set is shortly before emergence on the ceramic.
- a particularly simple way to bring about the transition from a substantially laminar flow into a substantially turbulent flow is that the controllable throttle cross-section between adjacent subspaces is formed by a pocket whose effective cross-section is reduced in the direction of rotation. D. h., By the pocket and the housing, in particular its pressure chambers limiting webs of the additional throttle cross-section is formed, the effective cross section changes depending on the angle of rotation.
- this ramp is formed approximately parallel to the axis.
- the ramp can be formed, for example, in the region of half the circumferential length of the pocket.
- the height of the ramp may be greater than the depth of the pocket after cross-sectional reduction.
- the pocket is designed with an approximately triangular base, so that the above-mentioned ramp is approximately parallel to a base edge of the triangular-shaped pocket.
- This executed with a ramp pocket can be formed on the piston or on the housing.
- the wings are each designed with a U-profile, each on one
- Web / radial projection is placed, depending on the direction of rotation of one of the U-legs in lateral contact with the radial projection and thus defines a throttle cross-section.
- the leadership of this wing on the radial projection is significantly simpler, since the U-configuration, the relative positioning between the radial projection and wing both constructive and mounting technology is much easier manageable than the tilting bearing of the sealing lip in the state of Technology.
- the webs / radial projections and thus the entire piston can be formed much more compact and with less material, with no receiving groove for a sealing lip or the like must be provided.
- a largely continuous U-leg of the wing covers the recesses formed in the radial projection so that they are ineffective in one direction of rotation.
- the other U-limb comes into operative engagement, on which throttle cross sections adapted to the recesses are formed, so that the additional flow cross section is effective. That Depending on the direction of rotation, one or the other U-limbs comes into abutment with the radial projection and thus determines the effective additional flow cross-section.
- the throttle cross section is formed in the end face region between a sleeve bottom and end face sections of the radial projections.
- the effective in the sense of a throttling surface of this throttle cross-section varies with the angle of rotation.
- This rotation angle dependence of the throttle cross-section can be formed, for example, by the fact that the bottom of the housing and / or the adjacent end faces of the radial projections are designed as Steuerkulissen.
- an additional throttle slot can be opened or closed between the two pressure chambers, whose cross section is determined by a throttle ramp. Through this additional throttle slot, a progressive damping in a damping direction can be provided.
- connection between the rotary piston and the housing is designed so that an axial play is provided. This can be done by securing it by means of a screw, in that it is not screwed to its final dimensions, but in such a way that an approximately floating mounting of the rotary piston in the housing is achieved in the axial direction. In this way, the friction of the system can be significantly reduced.
- Such floating storage can be achieved in principle with the alternative assurance by means of sleeve cover or the like.
- the device-technical effort to form the throttle ramp is minimal, while this is designed as pocket-shaped recess on the rotary piston.
- the progressive damping characteristic can then be achieved by the fact that the pocket-shaped recess tapers in a direction of rotation, so that upon rotation of the rotary piston in this direction the throttle slot is correspondingly reduced and thus the damping effect is increased.
- the rotary damper according to the invention can advantageously be used in toilet seat sets, wherein in each case a rotary damper is assigned to the toilet seat and the toilet lid.
- the rotary dampers are designed with different axial effective lengths.
- both the rotary piston and the housing receiving this can be provided with identifiers, so that the mounting safety is further improved.
- the rotary piston and the housing are rotatably connected to each other via an axial screw.
- This screw is cohesively, for example, secured by gluing or welding, so that on the one hand the assembly is extremely simple and on the other hand, an accidental release of housing and rotary piston is avoided.
- the aforementioned screw can be dispensed with if the rotary piston is secured in the housing via a sleeve cover.
- the securing of the rotary piston takes place in the housing in a form-fitting manner, wherein, for example, a bolt cooperating with the rotary piston is formed with a groove or the like into which then a securing element, for example a securing ring or a tangentially arranged split pin or the like, engages. to take the backup in the axial direction.
- a securing element for example a securing ring or a tangentially arranged split pin or the like
- All the above-described fuses can, as stated above, be formed with an axial clearance to reduce friction.
- the cohesive securing / connection can be done for example by gluing or welding.
- the seal between the rotary piston and the housing or a sleeve cover is effected by means of an elastic ring, for example a sealing ring.
- the geometry of the ring / sealing ring is preferably selected so that it generates less friction on the inner wall of the housing during the rotational movement, by applying only to these and can be ensured by suitable design that the relative movement on the outer diameter of the rotary piston, more precisely said on the notch base of the rotary piston side receiving groove for this sealing ring takes place. In this area, the friction is much lower, so that accordingly the wear is minimized and the damper stays tight longer.
- the rotary damper due to the much lower friction a more advantageous startup behavior. This means that the seat or lid starts a few degrees earlier, which in principle means significantly improved performance for the customer.
- FIG. 2 shows an exploded view of the damper from FIG. 1,
- FIG. 3 shows a longitudinal section through the damper according to FIG. 1,
- Figure 4 is an exploded view of another embodiment of a rotary damper according to the invention.
- Figure 5 is a sectional view of the rotary piston of the rotary damper according to Figure 4.
- FIG. 6 shows a detail B of the rotary piston from FIG. 5;
- Figure 9 two rotary damper for a toilet seat.
- the hydraulic rotary damper according to Figure 1 serves to dampen a lowering movement of a toilet seat set.
- a rotary damper 1 has a housing 2, in which a rotary piston 4 is rotatably guided.
- the housing 2 has at one end portion an adapter piece 6, in which acount8 is formed, in which extends when mounting the toilet seat a connected to the ceramic pin inside.
- the housing 2 further has a sleeve portion 10, in which the rotary piston 4 described in more detail below is guided. This has a partially visible in Figure 1 sealing collar 12, which seals the sleeve portion 10 to the outside.
- FIG. 2 shows the rotational damper 1 according to FIG. 1 in an exploded view. It can be seen the housing 2 with the adapter piece 6 and the sleeve section 10 embodied in one piece therewith and a receiving space 18 encompassed by the sleeve section 10 for the rotational damper 1.
- the sealing collar 12 has on its outer circumference an annular groove 20 into which a sealing ring, for example, an O-ring 22 is used.
- a piston portion 24 connects, which dips into the receiving space 18.
- a further O-ring 26 is arranged with a significantly smaller diameter than the aforementioned O-ring 22 to seal the pressure chambers described below.
- the piston portion 24 has two radial projections 28, 30 arranged diametrically opposite one another, the outer diameter of which is smaller than the inner diameter of the receiving space 18.
- At the two radial projections 28, 30 are each two outwardly opening recesses 32, 34 and 36, 38 are formed.
- On the outer peripheral edges of the radial projections 28, 30, a respective wing 40, 42 is placed, which seen in the axial direction has an approximately U-shaped profile, wherein two throttle openings 44, 46 are formed on one of the U-legs, while the other U -Skeleton 52, 54 is executed consistently.
- the geometry of the two throttle cross sections 44, 46 and their spacing corresponds to the geometry of the recesses 32, 34; 36, 38.
- the distance between the two legs of the wings 40, 42 is slightly wider than the width b of the radial projections 28, 30 carried out, so that the two wings 40, 42 are guided in the circumferential direction with play on the radial projections 28, 30.
- the two U-legs connecting top surface 48, 50 of the wings 40, 42 is convex and is sealingly against the inner peripheral wall of the sleeve portion 10 at.
- the two U-legs of the wings 40, 42 are formed such that in a rotational direction of the continuous U-legs 52, 54, the two associated recesses 32, 34 and 36, 38 sealingly covers, while in the other direction of rotation, the recesses 44, 46 of the other U-legs overlap with the recesses 32, 34 and 36, 38, so that a flow cross-section is opened, via which the pressure medium through the recesses and through a gap between the radial web 28, 30 and the continuous leg 52, 54 can flow from one pressure chamber into the adjacent pressure chamber.
- the rotary piston 4 is furthermore designed with an axial bore 60 through which a screw 56 extends, via which the rotary piston 4 is connected to the housing 2.
- this screw 56 extends with its end section into the region of the attachment. grip recess 16 into it.
- a nut 58 can be used, which comes with the screw 56 in threaded engagement.
- FIG. 3 shows a longitudinal section through the mounted rotary damper 1. It can be seen the housing 2 with the adapter piece 6 and the sleeve portion 10, in which the rotary piston 4 is immersed. This is in the assembled state with its sealing collar 12 and the O-ring 22 on the inner peripheral wall of the sleeve portion 10 at.
- the screw 56 passes through the axial bore 60 and dives with its screw head in a corresponding extension of the axial bore 60 a.
- the other end portion extends into the region of the access recess 16 and is screwed to the nut 58.
- a problem with such a screw connection is that it can come loose due to the relative rotation of housing 2 and rotary piston 4.
- the screw connection between the nut 58 and screw 56 is secured by means of a cohesive screw lock, for example an adhesive. This fuse can be attached with minimal effort through the access opening 16 and requires virtually no changes in the housing 2 or the rotary piston. 4
- screw lock can be used.
- the screw 56 and the nut 58 are not screwed to final dimensions, so that a certain axial clearance between rotary piston 4 and housing 2 is allowed. This allows the frontal friction and thus the frontal wear compared to conventional solutions that are bolted to final dimensions, be significantly reduced. By the measures described above, the mounting safety of the rotary damper can be significantly improved.
- FIG. 2 Indicated in FIG. 2 are two webs 62, 64 which project radially inwardly from the inner peripheral wall of the sleeve section 10 and extend as far as the outer circumference of the piston section 24 in the region between the two radial projections 28, 30 and bear sealingly thereon.
- These webs 62, 64 of the embraced by the sleeve portion 10 space is divided into two pressure chambers 66, 68, which in turn are divided by the two radial projections 28, 30 into two subspaces.
- These two subspaces can be connected to each other in dependence on the position of the two wings 40, 42 via the throttle cross sections 44, 46 in order to provide an additional flow cross section and thus a reduced damping effect.
- Further throttle cross-sections are formed by a respective pocket 98 on the outer circumference of the rotary piston 4. This will be explained in more detail below.
- the actual throttling cross-section between the described spaces, which effects attenuation, is formed on the end face between the end faces of the two radial projections 28, 30 and a frontal bottom 70 of the sleeve section 10.
- This bottom is designed with a control link 72, so that a throttle gap between the bottom 70 and the end faces of the radial projections 28, 30 in dependence on the course of the control link 72 and in dependence on the rotation angle is variable and the damping effect is changed depending on the direction of rotation.
- the effective throttle cross-section is minimal, while in the areas in which a relatively fast movement is possible, for example, when lifting or at the beginning of Lowering movement, a comparatively large throttle cross-section and thus a high speed is possible.
- the above-mentioned flow cross-section is additionally controlled by the wings 40, 42.
- the hydraulic rotary damper according to the invention is characterized by an extremely simple construction with superior function.
- throttling cross sections 44, 46 are formed in one of the U legs 52, 54, while in the opposite U legs 52, 54 no throttle cross sections are provided, so that the recesses 32, 34, 36, 38 of the radial projections 28 , 30 in which one direction of rotation is covered by the "closed" U-leg and thus only the comparatively small end throttle section is effective.
- cooperating throttle cross-sections 44, 46 are executed in order to influence the pressure medium flow and thus the speed of movement in the raising or lowering direction.
- the rotary piston 4 is secured in the housing 2 via the screw 56.
- Figure 4 shows an embodiment in which can be dispensed with such a screw, since the rotary piston 4 is fixed by means of a sleeve cover 74 in the housing 2, wherein in the illustrated embodiment, this sleeve cover 74 is materially connected to the housing 2 such that the Rotary piston 4 is still rotatable.
- the basic construction of the rotary damper 1 according to FIG. 4 largely corresponds to the exemplary embodiment described above, so that in this respect only some of the components are discussed and, incidentally, reference may be made to the above description.
- the material-locking fuse can be designed so that the rotary piston 4 is mounted with a certain axial play in the housing 2 in order to reduce the friction.
- the housing 2 also has an integrally formed thereon adapter piece 6, in which the blind hole 8 is formed for placement on a hinge pin or the like.
- the sleeve portion 10 is arranged coaxially to the adapter piece 6 and forms the receptacle for the rotary piston 4.
- a circumferential groove 76 is formed, which is also provided in the embodiments described above.
- the rotary damper may be secured, for example in a mounting strap a toilet seat.
- the rotary piston 4 is again executed in this embodiment with a two-flat 14 having a certain axial length F, which is adapted to a corresponding recess in the relevant fastening tab, so that a rotationally fixed connection between rotary piston 4 and the toilet seat or the toilet seat Lid can be produced.
- the annular groove 20 is formed, in which the O-ring 22 is used during assembly. About this the damping chamber is sealed to the outside.
- the rotary piston 4 has a sealing collar 12 which rests sealingly with its outer periphery on the inner peripheral wall of the not visible in Figure 4 receiving space of the sleeve portion 10. Following this sealing collar 12 extends in the axial direction of the piston portion 24 with the two radial projections 28, 30, on each of which a wing 40, 42 is guided. These are each formed with the U-legs 52, 54.
- the U-leg 54 is designed to be continuous, while in the U-leg 52, the two throttle cross-sections 44, 46 are provided.
- a Schenkelaus Principleung 78 is provided between the two throttle cross-sections 46, 44, whose importance will be discussed later.
- the end portion of the rotary piston 4 remote from the two-bladed 14 is set back radially in the exemplary embodiment according to FIG. 4 and forms a guide pin 80 which dips into the housing in a guide recess 82 (see FIG. 5) so that the rotary piston is centered with respect to the housing 2 is guided.
- a laterally projecting cam 84 is provided in each case (in the illustration according to FIG Cam 84 visible), which dips into the respective leg recess 78 of the associated vane 40, 42, so that the wings are also secured in the axial direction.
- the sleeve cover 74 has, according to the representation according to FIG. 4, an outer flange ring 86 which rests on the front side at the mouth of the sleeve section 10.
- a centering 88 extends into the receiving space 18 (not visible in Figure 4) of the sleeve portion 10 and engages around the rotary piston 4 in the region of the annular groove 20, so that the assembled O-ring 22 sealingly on an inner circumferential wall 90 of the flange 86 is present.
- the sleeve cover 74 is, as will be explained in more detail with reference to Figures 5 and 6, with the sleeve portion 10 and thus welded to the housing 2.
- a welding stage 92 is formed on the outer periphery of the centering portion 88.
- identifiers "L" are provided on the two-bladed surface 14 of the rotary piston 4 and on the adapter piece 6 of the housing 2, indicating the assignment of the rotary piston 4 to the housing 2 during assembly of the rotary damper and assembly of the rotary damper in the toilet seat or simplify the toilet lid, so that a confusion of components is prevented.
- the preparation of the rotary piston 4 and the housing 2 can be done for example by injection molding. Since considerable quantities are manufactured, the use of multiple tools can be advantageous in each of which the components of the lid damper or the seat damper a toilet seat set are made. By the identifier "L” or "R” then a confusion of the components can be prevented during mounting.
- FIG. 5 shows the rotary piston 4 of the exemplary embodiment according to FIG. 4 in a three-dimensional individual representation.
- the cam 84 As described, in the region between the two recesses 32, 34 and 36, 38 of the two wings 28, 30 respectively formed the cam 84, wherein in the illustration of Figure 5, the cam between the recesses 32, 34 is not visible and after stands out at the back from the drawing plane.
- two of the abovementioned pockets 98 are formed in the circumferential direction adjacent to the respective cam 84 on the piston section 24. The second pocket 98 is not visible in the illustration according to FIG. 5, since it lies on the rear side of the piston section 24.
- Each pocket 98 forms an approximately triangular base surface in the radial direction and tapers away from the radial projection 28 in the direction of the other radial projection 30 at the bottom.
- a base edge 100 (FIG. 6) of the triangular pocket 98 extends parallel to it Axial direction of the radial projection 38.
- the depth of the pocket 98 in the direction of the tip 102 of the pocket 98 also decreases.
- this has a stepped ramp 99, via which the depth of the pocket 98, d. h., The radial extent is reduced in the piston portion 24 "abruptly" toward the tip 102 out.
- FIG. 7 shows a schematic section along the line A-A through the pocket 98 in FIG. It can be seen that the bag 98 is subdivided into a region with a relatively large radial depth T and a region with a comparatively small radial size t by a stepped ramp 99.
- the region with a greater radial depth T is referred to below as the laminar chamber 103 and the region with a smaller radial depth t as the turbulence chamber 101.
- the height H of the ramp 99 is more than half of the depth T of the laminar chamber 103, so that over this ramp 99, a very strong cross-sectional reduction of the formed by the pocket 98 throttle gap.
- the ramp 99 is located approximately in the half of the circumferential extent of the entire pocket 98.
- the depth t of the turbulence chamber 101 decreases towards the tip 102, so that Driving through the step-shaped throttle cross-section reduction this then already quite small throttle cross-section continues to decrease with the pivoting towards the support position on the ceramic.
- the depth T of the laminar chamber 103 may also decrease continuously from the base edge 100 to the ramp 99.
- Fig. 8a shows the rotational angular position which the rotary piston in an open set, i. for example, occupies a raised seat.
- the rotary piston 4 rests with its radial projections 28, 30 on the webs 62, 64, wherein the system takes place in each case via the frontally arranged cams 84 of the webs 28.
- the throttle slots 108, 1 10 are not open to the respective adjacent pressure chamber 66, 68.
- a predetermined pivoting range for example, begins at about 30 ° before placing the toilet seat on the ceramic
- the effective throttle cross-section is suddenly reduced by means of the ramp 99 of the pockets 98 - this leads to that the laminar flow turns into a turbulent flow, wherein the pressure medium is displaced from the decreasing pressure chamber 68 in the adjacent increasing pressure space and thereby arise due to the turbulent flow in the decreasing pressure vortex wakes 105 (see Figure 8b), through which Pressure in the housing 2 is reduced.
- the rotary damper 1 increases due to the increased flow resistance applied by the rotary damper 1, the toilet seat support torque, so that the lowering is slowed down and the toilet seat set gently on the ceramic.
- this supporting torque level When reversing the throttle cross section via the ramp 99, this supporting torque level abruptly increases by up to 2.5 times, at the same time the pressure in the housing is lowered by about one third.
- the maximum force is applied to the radially extending surface of the ramp 99.
- the pressurization of the damper housing 2 is significantly reduced compared to the conventional solutions, so that the risk of damage to the rotary damper in continuous operation is significantly reduced.
- the ramp geometry described generates, according to the above, an additional damping effect, which is accompanied by a simultaneous reduction in pressure in the damper housing.
- the choke slots 108, 110 are completely closed, since the two recesses 98 are no longer in register with the two webs 62, 64.
- the wings 42, 44 with the continuous U-legs 54 are then in contact with the webs 62, 64.
- the throttle cross-sections 46, 48 of the wings 40, 42 are then correspondingly opened, so that the throttle effect when opening is minimal and this toilet seat set can be easily raised.
- a rotary damper in which a controllable throttle cross-section between a decreasing pressure chamber and an increasing pressure chamber is formed so that the effective throttle cross-section decreases abruptly.
- the throttle cross-section may otherwise be configured so that, after a predetermined angle of rotation, an envelope of a laminar flow of the pressure medium displaced from a decreasing pressure chamber into a turbulent flow takes place.
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- Health & Medical Sciences (AREA)
- Public Health (AREA)
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Toilet Supplies (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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ATA9004/2016A AT524746B1 (de) | 2015-01-26 | 2016-01-25 | Hydraulischer Rotationsdämpfer |
DE112016000473.7T DE112016000473B4 (de) | 2015-01-26 | 2016-01-25 | Hydraulischer Rotationsdämpfer |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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DE102015101083.6 | 2015-01-26 | ||
DE102015101083 | 2015-01-26 | ||
DE102015112160.3A DE102015112160A1 (de) | 2015-01-26 | 2015-07-24 | Hydraulischer Rotationsdämpfer |
DE102015112160.3 | 2015-07-24 |
Publications (1)
Publication Number | Publication Date |
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WO2016120205A1 true WO2016120205A1 (de) | 2016-08-04 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/EP2016/051445 WO2016120205A1 (de) | 2015-01-26 | 2016-01-25 | Hydraulischer rotationsdämpfer |
Country Status (3)
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AT (1) | AT524746B1 (de) |
DE (2) | DE102015112160A1 (de) |
WO (1) | WO2016120205A1 (de) |
Cited By (4)
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WO2018165840A1 (zh) * | 2017-03-14 | 2018-09-20 | 游章森 | 马桶盖阻尼器的结构 |
CN108852133A (zh) * | 2018-06-27 | 2018-11-23 | 宁波博帆卫浴有限公司 | 一种分段缓降铰链 |
DE102016105880B4 (de) * | 2015-12-10 | 2021-01-21 | Hamberger Industriewerke Gmbh | Hydraulischer Rotationsdämpfer |
DE102016113670B4 (de) | 2016-07-25 | 2023-10-26 | Hamberger Industriewerke Gmbh | Hydraulischer Rotationsdämpfer und WC-Sitzanordnung |
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Publication number | Priority date | Publication date | Assignee | Title |
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DE102017105310B4 (de) | 2016-10-21 | 2019-07-11 | Hamberger Industriewerke Gmbh | Rotationsdämpfer, Lichtkappe und WC-Sitzgarnitur |
JP6801905B2 (ja) * | 2017-05-11 | 2020-12-16 | 株式会社Tok | 簡易自立機構を備える回転ダンパ |
DE102018116187A1 (de) * | 2018-07-04 | 2020-01-09 | Inventus Engineering Gmbh | Drehdämpfer |
US11072958B2 (en) * | 2018-08-07 | 2021-07-27 | Kem Hongkong Limited | Damper hinge and western-style toilet using the same |
CN109578508B (zh) * | 2018-12-05 | 2023-04-14 | 厦门瑞尔特卫浴科技股份有限公司 | 一种具有后仰静音功能的阻尼机构 |
IT201900002843A1 (it) * | 2019-02-27 | 2020-08-27 | Brera Cerniere Srl | Elettrodomestico |
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DE10313394B4 (de) * | 2003-03-25 | 2005-02-24 | Pagette Sanitär Produktions- und Vertriebsgesellschaft mbH | Dämpfungseinrichtung |
CN201219865Y (zh) | 2008-04-30 | 2009-04-15 | 厦门豪帝卫浴工业有限公司 | 一种阻尼装置 |
WO2011050517A1 (zh) | 2009-10-28 | 2011-05-05 | Liu Zhifang | 阻尼机构 |
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JP3053583B2 (ja) * | 1996-12-20 | 2000-06-19 | トックベアリング株式会社 | 二連式回転ダンパ |
JP2009293697A (ja) * | 2008-06-05 | 2009-12-17 | Nifco Inc | ダンパー |
JP2011212133A (ja) * | 2010-03-31 | 2011-10-27 | Toto Ltd | 便座装置 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016105880B4 (de) * | 2015-12-10 | 2021-01-21 | Hamberger Industriewerke Gmbh | Hydraulischer Rotationsdämpfer |
DE102016113670B4 (de) | 2016-07-25 | 2023-10-26 | Hamberger Industriewerke Gmbh | Hydraulischer Rotationsdämpfer und WC-Sitzanordnung |
WO2018165840A1 (zh) * | 2017-03-14 | 2018-09-20 | 游章森 | 马桶盖阻尼器的结构 |
CN108852133A (zh) * | 2018-06-27 | 2018-11-23 | 宁波博帆卫浴有限公司 | 一种分段缓降铰链 |
CN108852133B (zh) * | 2018-06-27 | 2023-09-22 | 宁波博帆卫浴有限公司 | 一种分段缓降铰链 |
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DE102015112160A1 (de) | 2016-07-28 |
DE112016000473B4 (de) | 2023-05-11 |
AT524746B1 (de) | 2022-11-15 |
AT524746A5 (de) | 2022-08-15 |
DE112016000473A5 (de) | 2017-10-05 |
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