WO1999032799A1 - Element ressort - Google Patents

Element ressort Download PDF

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Publication number
WO1999032799A1
WO1999032799A1 PCT/EP1998/008188 EP9808188W WO9932799A1 WO 1999032799 A1 WO1999032799 A1 WO 1999032799A1 EP 9808188 W EP9808188 W EP 9808188W WO 9932799 A1 WO9932799 A1 WO 9932799A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
spring element
element according
piston
tube
Prior art date
Application number
PCT/EP1998/008188
Other languages
German (de)
English (en)
Inventor
Hermann Krautkrämer
Original Assignee
Krautkraemer Hermann
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE1997156557 external-priority patent/DE19756557A1/de
Application filed by Krautkraemer Hermann filed Critical Krautkraemer Hermann
Priority to AU19682/99A priority Critical patent/AU1968299A/en
Priority to DE19881964T priority patent/DE19881964D2/de
Priority to EP98964516A priority patent/EP1040282A1/fr
Priority to DE29880118U priority patent/DE29880118U1/de
Publication of WO1999032799A1 publication Critical patent/WO1999032799A1/fr

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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
    • 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
    • F16F9/32—Details
    • F16F9/36—Special sealings, including sealings or guides for piston-rods
    • 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
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F16F9/0209—Telescopic
    • 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
    • F16F9/32—Details
    • F16F9/43—Filling or drainage arrangements, e.g. for supply of gas
    • 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
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • 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
    • F16F2226/00—Manufacturing; Treatments
    • F16F2226/02—Surface treatments

Definitions

  • the present invention relates to a spring element, in particular a gas spring or a hydraulic spring, and the production thereof.
  • a gas spring is a hydropneumatic adjustment element with a self-contained gas and oil system as an energy store.
  • the spring force is generated by a compressed filling medium.
  • the principle of gas springs is based on the compressibility of a gas volume enclosed in a container.
  • Gas springs can be designed both as gas pressure springs and as gas tension springs.
  • the structure of a conventional gas spring is described below using an example of a conventional gas pressure spring.
  • These consist essentially of a cylindrical pressure tube, which is sealed gas-tight on one side with a cover and on the opposite side by a sealing and guide package.
  • a piston rod is axially movably guided by the seal and guide package, at the end of which a piston is fastened inside the pressure tube and at the same time limits the extension of the piston rod.
  • the outer end of the piston rod and the pressure pipe end are each provided with a fastener adapted to the application.
  • the desired spring insertion and extension force of the piston rod of a gas spring is achieved by introducing a certain excess gas pressure into the cylindrical pressure tube. Furthermore, the cross-sectional area of the piston, on which the pressure in the cylindrical pressure tube acts, is important for determining the desired spring insertion and extension force.
  • the piston rod and the piston of a gas spring are pushed in or out, the volume space of the gas is reduced and an increase in pressure, which is a measure of the increase in the potential energy for the respective position, is brought about.
  • the piston in the interior of the gas spring has the function of enabling a specific extension speed, effecting damping adapted to the application, serving as a guide element and limiting the extension width of the piston rod.
  • Piston designs are known in which the piston is provided with one or more small nozzle bores or with a labyrinth system. When using such a piston, a targeted damping when pushing the piston rod in and out can be achieved by the overflow of gas.
  • the spring characteristic of a conventional gas spring is shown in the force-displacement diagram (F-s diagram).
  • the force curves follow approximately a straight line and have a slight increase in force over the spring travel compared to coil springs.
  • the breakaway force which characterizes the force with which the piston rod must be released at the beginning of a movement, is usually not shown in the F-s diagram. This breakaway force is usually a multiple of the initial insertion or extension force.
  • the spring characteristic of the conventional gas spring can be changed, for example, by introducing oil.
  • An increased oil quantity inside the gas spring causes increased insertion and extension forces.
  • the spring characteristic can be varied by changing the dimensions of the pressure pipe and the piston rod.
  • a further possibility for influencing the spring characteristic is to provide a spring element in the volume space, whereby the spring characteristic of the gas spring is superimposed on that of the spring element.
  • the piston rod must be hardened and have a maximum roughness depth of approximately 1 to 3 ⁇ m. To do this, it is conventionally ground, surface hardened and chrome-plated.
  • a salt bath hardening method Another method that can be used as an alternative to chrome plating is a salt bath hardening method.
  • the piston rods are placed in a salt bath on e.g. Heated to 580 ° C and remain in it for a certain time. This process is an ascent hardening process that also provides rust protection for the surface of the piston rod. After the piston rods are removed from the salt bath, they have to be processed on a polishing machine in order to obtain the required surface quality.
  • the known gas springs and methods for their production have the particular disadvantages that their characteristic cannot be changed arbitrarily, the functionality of the gas spring is no longer guaranteed with the slightest damage to the piston rod or the tube, and high system pressures in the gas spring are required, as a result of which at elevated temperatures, for example in the event of vehicle fires, there is a considerable risk potential.
  • Further disadvantages are the high breakaway force of the piston rod, the complex manufacturing process of the piston rod and the associated environmental problems. In particular, environmentally harmful residues caused by the salt bath hardening process are problematic, as well as grinding and polishing residues or sludges, which as highly toxic special waste have to be disposed of in a very complex and expensive manner.
  • the hydraulic medium which is hardly or preferably not compressible, serves as the transmission medium.
  • a pressure or energy store must be provided for storing energy.
  • this is external, e.g. arranged in the form of a pressure vessel.
  • a specific application of hydraulic systems is e.g. to find on industrial robots.
  • There the hydraulic system is used to absorb deceleration forces when moving the robot arms. Due to the leakage problem of these hydraulic systems, use in many areas is not possible or only possible through complex, additional measures, such as in food production and processing or in pharmaceutical processing.
  • the present invention is therefore based on the object of an improved spring element, in particular an improved one To provide gas spring and an improved hydraulic spring and a corresponding manufacturing process. This object is achieved with the features of the claims.
  • the invention has the advantage that the spring can be designed as a multi-tube spring with at least one piston such that the sliding surfaces of the spring are safe from damage and the spring remains operational even in the event of external damage.
  • a compression spring according to the invention has, for example, an inner tube and an outer tube, preferably arranged concentrically around it, and a piston with a piston rod provided in the inner tube.
  • the two tubes define two volume spaces that are connected or connectable to one another via a control unit.
  • At least two tubes are to be provided for executing a tension spring according to the invention.
  • the tubes of the tension spring are advantageously arranged essentially concentrically.
  • At least two pipes define at least two volume spaces communicating with one another via a control device.
  • the inner volume space preferably has a constant volume, while the volume of the outer volume space, in which an annular piston is guided, is variable in accordance with the piston position.
  • the volumes of both volume spaces are variable.
  • the third tube is preferably arranged outside the tube defining the outer volume space in order to protect all sliding surfaces from contamination.
  • the spring of the present invention thus has the particular advantages that damage to components of the spring according to the invention which are accessible from the outside do not result in any functional impairment, their filling pressure can be reduced by up to 50% compared to conventional springs, their characteristic curve can be designed variably and the extension or the insertion speed of the piston can be set as desired. Furthermore, the springs according to the invention can be produced in an environmentally friendly manner since their components do not have to be subjected to any special processes in which environmentally harmful substances are produced.
  • the spring can furthermore have variable fastening means, have a clamping device for fixing the piston in any axial position and have means for damping the end position.
  • the springs according to the invention can be inexpensively, e.g. are manufactured from commercially available components, thereby achieving a further reduction in manufacturing costs and enabling use as a mass product.
  • the springs according to the invention can be used without problems even in heavily soiled or soiling systems. Leakage of oil, e.g. in conventional hydraulic systems, on the one hand by gas as the filling medium and on the other hand by using a closed hydraulic system, i.e. without hydraulic pressure accumulator, can be excluded, whereby the spring according to the invention also e.g. in places with high to highest demands on purity, e.g. can be used in the food, pharmaceutical or chemical industry, as well as in clean rooms.
  • Fig. 1 shows a first embodiment of an inventive
  • FIG. 2 shows a second embodiment of the invention
  • FIG. 3 shows a third embodiment of the invention
  • FIG. 4 shows a fourth embodiment of the invention
  • Fig. 5 shows a first embodiment of an inventive
  • FIG. 6 shows a second embodiment of the invention
  • FIG. 7 shows an embodiment of a hydraulic tension spring according to the invention.
  • the two-tube gas pressure spring 2 of the present invention essentially has an inner tube 4 and an outer tube 6 arranged essentially coaxially therewith.
  • a piston 8 which is slidably mounted in the inner tube 4.
  • the piston 8 is connected to a piston rod 10, for example by a thread, but preferably by a crimp or crimp connection.
  • a guide element 14 is provided on a first end 12 of the tubes 4 and 6, which guides the piston rod 10, preferably simultaneously seals the inner tube 4 with respect to the outer tube 6 and has means 16 against the ingress of dirt from the outside.
  • the opposite end 18 is closed by a control unit 20.
  • the inner tube 4, the piston 8 and the control unit 20 thus form a first volume space 22.
  • the annular space between the inner tube 4 and the outer tube 6 forms together with the guide element 14 and the control unit 20 a second volume space 24.
  • the two volume spaces 22 and 24 are connected or connectable by the control unit 20 by the control unit 20 having a control slot 26, which is preferably communicates with an annular channel 28.
  • the dimensions of the control slot 26 and the annular channel 28 define the extension speed of the piston rod 10.
  • the volume spaces 22 and 24 are filled with gas, preferably with nitrogen, through a radial gas filling hole 30. Both volume spaces 22 and 24 are thus subjected to the same gas pressure.
  • the gas filling bore 30 is closed with a closure 32, which also acts as a burst protection for the two-pipe gas pressure spring 2.
  • the closure 32 is preferably in the form of an annular elastic element e.g. made of rubber, which is arranged within the gas filling bore 30, so that when the two-tube gas pressure spring 2 is filled, the closure 32 is pressed inwards, while the pressure of the gas then presses the closure 32 onto the gas filling bore 30 and seals. If the pressure inside the spring increases excessively, e.g.
  • the piston 8 of the two-pipe gas pressure spring 2 is provided with a groove-ring sleeve 34, which has a V-shaped groove, as a result of which the system pressure in the first volume space 22 acts on the groove-ring sleeve 34 and the sealing effect is intensified .
  • the groove-ring sleeve 34 is firmly connected to the piston 8 by means of a retaining washer 35 and a support ring 37, for example by riveting, screwing, gluing or other known fastening measures. This has the effect that the groove-ring sleeve 34 seals the piston 8 tightly against the inner tube 4.
  • the term “firmly seated” means in particular that relative rotations are not possible between the piston 8 and the groove-ring sleeve 34, or only by applying large forces.
  • the piston rod 10 is provided at one end opposite the piston 8 with a connecting element 36, which can be designed differently depending on the application.
  • a connecting element 36 which can be designed differently depending on the application.
  • the outer tube 6 or the control unit 20 has a connecting element 38, which can be designed flexibly depending on the application.
  • the two volume spaces 22 and 24 are acted upon by the same system pressure via the gas filling opening 30.
  • the piston 8 and the piston rod 10 are brought into an extended basic position by the system pressure. If the piston rod 10 is pushed in, the piston 8 moves in the inner tube 4 in the direction of the control unit 20 and thus reduces the volume of the first volume space 22. As a result, the gas flows from the first volume space 22 through the control unit 20 into the second volume space 24 and is preloaded .
  • the piston rod is relieved, it is pushed out by the prestressed gas pressure in the second volume space 24 at a precisely defined extension speed. This extension speed is defined by the cross section of the ring channel 28 and the control slot 26.
  • Gas pressure springs are used in particular in driving and aircraft, chairs and any machines.
  • a typical one Application examples can be found on tailgates, bonnets or seats in motor vehicles.
  • O-rings are preferably used to seal the two volume spaces 22 and 24 against one another on the guide element 14 and on the control unit 20.
  • the sealing means 16 is also preferably designed as an O-ring.
  • Another O-ring is provided on the piston 8 for the same purpose.
  • the two-tube gas spring 2 shown in Figure 2 shows a second embodiment of the invention.
  • the connecting element 38 is not located on the control unit 20 but on the outer tube 6 of the two-tube gas pressure spring 2.
  • the connection between the first volume space 22 and the second volume space 24 is in the control unit 20 by a spiral control slot 40 and the annular channel 28 bound.
  • a spring element 44 in the form of a helical compression spring is located in an annular space 42 between the guide element 14 and the piston 8 in order to dampen the piston rod 10.
  • any other compressible medium for damping could be used instead of the coil spring.
  • the third embodiment of the two-tube gas pressure spring 2 of the invention shown in FIG. 3 essentially corresponds to the gas spring described in FIGS. 1 and 2.
  • the piston 8 is provided with a quad ring 46 as a dynamic seal.
  • the guide element 14 is also designed to receive a clamping device 48.
  • This clamping device 48 consists of an annular clamping wedge 50, an annular pressure piece 52 and a nut 54 which can be screwed onto the guide element 14 and thus clamps the annular clamping wedge 50, whereby the piston rod 10 is clamped.
  • all other known embodiments of clamping devices for fixing the piston rod 10 to the springs according to the invention can also be provided.
  • any damage to the piston rod or the outer tube 6 of the two-tube gas pressure spring according to the invention does not impair the operation in the slightest, since the surface quality of the piston rod and the nature of the outer tube 6 are unimportant for the function and no gas-sealing effect is achieved on them or by them.
  • Fig. 4 shows a further embodiment of the gas spring according to the invention.
  • the fastening of the groove-ring sleeve 34 by means of the retaining disc 35 and the support ring 37 is shown.
  • the piston rod 10 is connected to the piston 8 by a crimp or crimp connection 56 in order to obtain an inexpensive connection.
  • control device 20 is modified in such a way that an overflow bore 58 is provided in the ring channel 28, which is sealed with a preferably circumferential sealant 60, e.g. a flat sealing ring, is sealable.
  • a preferably circumferential sealant 60 e.g. a flat sealing ring
  • the sealing means 60 rests on the overflow bore 58 and seals it, so that the extension characteristic, as with respect to the above embodiments, e.g. is predetermined by the ring channel 28 and / or control slot 26.
  • a further sealing element 62 is provided between the inner tube 4 and the control device 20 in order to seal the two volume spaces 22 and 24 in a gas-tight manner.
  • the spring element 44 is held in the guide element 14, preferably under prestress, for damping the end position of the spring 2.
  • a retaining ring 64 is provided in the guide element 14, which fixes the inner tube 4 and at the same time carries a support disk 66, on which the spring element 44 acts. If the piston 8 is moved near its end position when it is pushed out, it strikes the support disk 66 and lifts it against the spring force of the spring element 44 from the retaining ring 64, so that it moves in a damped manner to its end position.
  • a brake ring 68 is additionally provided between the support disk 66 and the spring element 44 in order to move the piston 8 braked into the end position.
  • a further support disk 70 is then preferably provided between the brake ring 68 and the spring element 44.
  • the brake ring 68 is preferably made of plastic, such as rubber, and is installed dry.
  • the two-pipe gas springs shown in the various embodiments are gas pressure springs.
  • the idea on which the invention is based can also be used for gas tension springs.
  • the guide element 14 can simultaneously be designed as a control unit and the annular space 42 represents the first volume space.
  • the guide element 14 of the two-tube gas spring only serves to better guide the piston rod 10, but is not a mandatory component.
  • the second volume space 24 can only be closed, e.g. through an annular lid.
  • the control unit 20 can instead of the control slot 26 and the annular channel 28 also be formed by a valve with which the passage cross section can be varied.
  • a gas spring according to the invention can also have further volume spaces by providing additional tubes. Their precise design should then be carried out, for example, in accordance with what has been described above, as shown in FIGS.
  • a three tube gas tension spring 102 of the present invention is shown in Figures 5 and 6. It essentially has an inner tube 104, a middle tube 106 and an outer tube 108.
  • the tubes 104, 106 and 108 are arranged essentially coaxially to one another with respect to a central axis 110.
  • the tubes 104, 106 and 108 are preferably cylindrical tubes, the wall thickness of which can vary according to the application.
  • the wall thickness of the inner tube 104 and the middle tube 106 are, for example, between 0.1 and 10 mm, preferably between 0.5 and 5 mm.
  • the inner tube 104 is connected at its first axial end to a terminating element 112 in a gas-tight manner.
  • This connection can be, for example, a screw connection with a corresponding seal or an adhesive, but the inner tube 104 and the end element 112 are preferably connected to one another by friction welding.
  • the closure element 112 has a gas filling bore 114 which opens into the interior of the inner tube 104.
  • a closure device 116 is provided at the second axial end opposite the first axial end of the inner tube 104.
  • the closure element 116 is connected to the inner tube 104 in a gas-tight manner by suitable sealing means 118.
  • the inner tube 104 thus forms a first volume space 120 with a constant volume through the closure element 112 and the closure device 116.
  • the volume space 120 is connected to a second volume space 124 by a control device 122, which is preferably formed in the form of at least one gas transfer hole.
  • the second volume space 124 is defined by the inner tube 104, the middle tube 106, an annular element 126 arranged at the second end of the inner tube 104 and by an annular piston 128.
  • the ring element 126 and the ring piston 128 are sealed gas-tight against the adjacent tubes 104 and 106 by means of sealing elements 130 and 132, respectively.
  • the center tube 106 of the throttle cable according to the invention the connection to the ring piston 128 thus simultaneously represents the piston rod.
  • the two volume spaces 120 and 124 are connected or connectable to one another by the control device 122, in that the control device 122 has at least one gas transfer hole or a gas transfer slot.
  • the insertion and removal speed of the piston rod can be defined by changing the dimensions of the control device.
  • the volume spaces 120 and 124 are filled with gas, preferably with nitrogen, as already explained above with reference to FIGS. 1 to 4, through the gas filling bore 114. Both volume spaces 120 and 124 are connected to the same by means of the control device 122 Gas pressure applied.
  • the gas filling bore 114 is closed with a closure 134 (only shown schematically), which at the same time acts as a burst protection for the gas tension spring according to the invention.
  • the closure 134 is preferably realized in the form of an annular elastic element, for example made of rubber, which is arranged within the gas filling bore 114, so that when the three-pipe throttle cable is filled, the closure 134 is pressed inwards, while the pressure thereafter of the gas presses the closure 134 onto the gas filling bore and seals it.
  • the sealing means 130 and 132 provided on the ring element 126 and ring piston 128 are preferably groove-ring sleeves which have a V-shaped groove, as a result of which the system pressure in the second, outer volume space 124 acts on the groove-ring sleeve, and the sealing effect is reinforced.
  • sealants 130 and 132 preferably contain or consist entirely of polytetrafluoroethylene (PTFE).
  • PTFE polytetrafluoroethylene
  • This material is highly anti-adhesive, has a low sliding and static friction coefficient and therefore no "stick-slip" effect.
  • PTFE is in a wide temperature range, i.e. Can be used from around -200 to + 270 ° C and has the highest chemical resistance.
  • the ring element 126 and the closure device 116 are formed as two parts, these could also be integral, i.e. be provided in one piece.
  • a mounting device 136 is provided on the middle tube 106 serving as a piston at its end opposite the annular piston 128, by means of which the gas tension spring 102 according to the invention can be connected to various connecting elements that are specific to the application.
  • the terminating element 112 is also designed to be able to be coupled to various connecting elements.
  • the outer tube 108 of the gas spring according to the invention is arranged concentrically with the two inner tubes 104 and 106 by means of the closure element 112.
  • the outer tube 108 is preferably connected to the end element 112 by friction welding.
  • a stripping device 138 is provided, with which dirt particles which are attached or adhering to the center tube 106 can be stripped off.
  • the scraper device 138 also has a device 140 against penetration of fine dirt particles or liquids.
  • the device 140 is preferably a sealant, such as an O-ring or felt ring.
  • At least one further device 142 or 144 against the ingress of dirt and liquids is preferably provided on the annular piston 128 and on the ring element 126 in order to ensure the operability of the gas tension spring 102 in accordance with the invention.
  • the arrangement of the outer tube 108 with the scraper device 138 and the devices 140, 142 and 144 ensures that the gas tension spring 102 according to the invention is protected against contamination on all sliding surfaces, so that it can be used even in dirty or heavily polluting systems and still has a long service life.
  • the two volume spaces 120 and 124 are acted upon by the same system pressure via the gas filling opening 114. Due to the system pressure, the annular piston 128 and thus the central tube 106 representing the piston rod are brought into a retracted basic position. If the piston rod 106 is pulled out, the annular piston 128 moves between the inner tube 104 and the central tube 106 in the direction of the control device 122 and thus reduces the volume of the second volume space 124. As a result, the gas flows from the second volume space 124 through the control device 122 into the first Volume space 120 and is further biased.
  • the piston rod 108 When the piston rod 108 is relieved, it is pushed in by the increased gas pressure in the first volume space 120 at a precisely defined insertion speed. This speed is defined by the opening, ie by the control device 122.
  • the control unit can tion 122 should be designed so that it does not represent too high a flow resistance to avoid heating. That means that in such a case the control device 122 should have at least one, but preferably a plurality of gas transfer bores or openings with a relatively large diameter.
  • Lubricating oil e.g. 1 to 8 cm, e.g. can be introduced into the volume spaces 120 and 124 together with the gas or is introduced during assembly of the gas tension spring.
  • FIG. 6 A modified embodiment of the gas tension spring 102 according to the invention is shown in FIG. 6.
  • the basic structure of the gas tension spring 102 is essentially identical to that previously described according to FIG. 5.
  • the gas tension spring 102 according to FIG. 6 differs, however, in that a piston 146 is provided in the first volume space 120, with which the volume of the volume space 120 can be varied.
  • the piston 146 is preferably guided so as to be axially movably adjustable via at least one threaded rod 148 with a screw head 150 in a thread in the end element 112.
  • the piston 146 is provided with sealing means (not shown) in order to seal the first volume space 120 from the annular space 152.
  • the F-s characteristic curve of the gas spring can be varied by means of a variable volume space 120.
  • the gas tension spring 102 shown in FIG. 6 can thus be used even more flexibly.
  • the gas tension spring 102 shown in FIG. 6 also has a connecting element 154 or 156 provided on the one hand on the terminating element 112 and on the other hand on the mounting element 136.
  • the connecting elements 154 and 156 are each mounted on the end element 112 or the mounting element 136 with the aid of a thread 158 or 160.
  • the thread 158 of the connection Element 154 is provided in a through hole so that the head 150 of the threaded rod 148 is easily accessible for adjusting the piston 146.
  • the thread 160 of the connecting element 156 on the opposite side is also provided in a through hole, so that a space 162 communicates with the surroundings via an opening 164.
  • the closure device 116 of the inner tube 104 is designed to be axially movable in the ring element 126 by means of a fine thread, so that it covers the control device 122 or its openings when the axial position is shifted in such a way that different flow cross sections and thus different flow speeds between the two volume spaces 120 and 124 cause can be.
  • the locking device 116 is adjusted through the bore 164 in the mounting element 136, through which a tool can be guided in order to engage a head 166 of the locking device 116 and to move the locking element 116 axially.
  • connection elements 154 and 156 are only shown by way of example. They can also be designed differently depending on the application or installation requirements. In the present case, transverse bores 168 and 170 are provided on the connecting elements 154 and 156 in order to mount the gas tension spring with a bolt in a machine (not shown).
  • any other conventional type of connection can also be provided. In particular, it can be preferred to form these elements in one piece or to produce them by welding individual parts, for example by friction welding.
  • an end stop means is provided in an annular space 172 formed between the inner tube 104 and outer tube 108 for damping the end position of the annular piston 128.
  • This end stop means is preferably a helical compression spring.
  • any other compressible damping medium such as an elastic rubber element, could be used instead of the coil spring.
  • Such an end stop means can also be provided in the second volume space 124, for example on the piston 128 or on the ring element 126.
  • the gas tension spring shown in FIG. 5 or 6 is further modified in that the outer tube 108 and also any other suitable component is designed to accommodate a clamping device (not shown).
  • This clamping device is similar to that described above with reference to Figures 1 to 4 and consists e.g. from an annular clamping wedge, an annular pressure piece and a nut which can be screwed onto the outer tube 108 and thus clamps the annular clamping wedge, whereby the piston rod or the central tube 106 is clamped.
  • all other known embodiments of clamping devices can also be provided for fixing the piston rod 106 to the gas tension spring 102.
  • any damage to the center tube 106 or the outer tube 108 of the three-tube gas tension spring 102 according to the invention does not affect the operation in the slightest, since the surface quality on the outside of the center tube 106 and the nature of the outer tube 108 are unimportant for the function and on them or by them no gas sealing effect is achieved.
  • the three-tube gas springs shown in the various embodiments are gas tension springs. However, the idea on which these embodiments of the invention are based can also apply by reversing the principle for gas pressure springs.
  • control device 122 can also be formed by a valve with which the passage cross section can be varied.
  • a gas spring according to the invention can also have further volume spaces by providing additional tubes. Their exact training should then be carried out in accordance with the previously described.
  • at least one pressure measuring device (not shown), which is connected to one of the volume spaces 120 and / or 124, can be provided in order to monitor the gas pressure or to feed it as a control input parameter.
  • the pressure measuring device can also be designed as a pressure switch. Such a pressure monitoring device is also possible for the embodiments described in FIGS. 1 to 4.
  • the inner tube 104 is joined to the end element 112 and then the outer tube 108 is also mounted on the end element 112. This can be done either by screwing threaded connections, by gluing, welding or other known, gas-sealing connection methods.
  • the inner tube 104 and the outer tube 108 are preferably welded to the end element 112 by friction welding.
  • the stripping device 138 can already be preassembled on the outer tube 108 or can be installed at a later time.
  • the piston rod or the center tube 106 is then mounted with the piston 128 and inserted into the annular space 172 between the inner tube 104 and the outer tube 108.
  • the closure device 116 and the ring element 126 are then mounted so that the two volume spaces 120 and 124 are sealed gas-tight from the environment.
  • the mounting element 136 is mounted on the center tube 106.
  • the volume spaces 120 and 124 can be filled with a gas pressure in accordance with the requirements for the gas spring. This method has already been explained above.
  • the sliding parts required for the gas spring according to the invention namely the inner tube 104 and middle tube 106 and the annular piston 126 can be produced from commercially available raw parts.
  • the surfaces of the sliding elements preferably have a roughness depth of 0.5 to 5 ⁇ m, but in particular a roughness depth of 1 to 3 ⁇ m is preferred.
  • FIG. 7 shows a further embodiment of a spring element according to the invention in the form of a hydraulic tension spring 202.
  • the structure of the hydraulic tension spring 202 essentially corresponds to the three-tube gas tension spring 102 described above with reference to FIGS. 5 and 6.
  • Three-tube tension spring 202 has an inner tube 204, a middle tube 206 and an outer tube 208. These tubes are preferably arranged essentially coaxially with one another with respect to a central axis 210.
  • the tubes 204, 206 and 208 are preferably cylindrical tubes, the wall thickness of which varies according to the application.
  • the wall thickness of the inner tube 204 and the middle tube 206 are, for example, between 0.1 and 10 mm, preferably between 0.5 and 5 mm.
  • the inner tube 204 is connected at its first axial end to a sealing element 212 in a fluid-tight manner.
  • the connection can be, for example, a screw connection with a corresponding seal, an adhesive or preferably a friction weld connection.
  • a closure device 214 for the inner tube 204 is provided at the second axial end opposite the first axial end of the inner tube 204.
  • the closure device 214 is connected to the inner tube 204 in a fluid-tight manner by means of suitable sealing means and / or a corresponding connection; the closure device 214 has an oil fill opening 216, which is preferably designed as an oil fill valve.
  • a vent valve 218 is provided in order to be able to discharge existing air when the hydraulic gas spring 202 is filled with hydraulic fluid.
  • a piston 220 is provided in the inner tube 204 so as to be axially movable.
  • the piston 220 has a stop projection 222 which bears against the closure device 214 when the hydraulic three-tube tension spring 202 according to the invention is in the inserted, ie relaxed, state.
  • the inner tube 204 with the closure element 214 and the piston 220 form a first annular volume space 224 formed around the stop projection 222.
  • a helical compression spring 226 is provided between the closure element 212 and the piston 220 which presses the stop projection 222 of the piston 220 against the closure device 214.
  • a guide pin 228 is preferably provided on the piston for fixing the coil spring 226.
  • Coil spring 226 may be a cylindrical helical compression spring as shown. However, it is also possible not only to provide a helical spring, but also to provide a plurality of nested helical compression springs with opposite coils. Furthermore, coil springs with changing wire cross-section and / or conical coil compression springs can also be provided. It is also possible to provide a gas pressure spring instead of the coil spring. When choosing the appropriate spring means 226 it is only important that it be able to absorb kinetic energy e.g. by storing or compressing a gas.
  • the first volume space 224 is connected to a second volume space 232 by a control device 230, which is preferably designed in the form of at least one fluid transition bore.
  • the second volume space 232 is defined by the inner tube 204, the middle tube 206, the closure device 214 and by an annular piston 234.
  • the Ver- Closing device 214 and the annular piston 234 are sealed in a fluid-tight manner with respect to the adjacent tubes 204 and 206 by means of sealing elements 236 and 238, respectively.
  • the central tube 206 of the hydraulic three-tube tension spring 202 thus simultaneously represents the piston rod due to the connection to the annular piston 234.
  • the two volume spaces 224 and 232 are connected or connectable to one another by the control device 230 in that the control device 230 has at least one gas transfer hole or a gas transfer slot.
  • the insertion and removal speed of the piston rod can be defined by changing the dimensions of the control device 230.
  • any pressure ratios can be set, so that the characteristic curve of the spring according to the invention can be adapted in the F-s diagram depending on the application.
  • the sealing means 236 and 238 provided on the annular piston 234 and on the closure device 214 are preferably groove-ring sleeves which have a V-shaped groove and are therefore superimposed by the system pressure in the second volume space 232 be so that the sealing effect is enhanced.
  • the groove-ring sleeves are non-rotatably on their respective seats.
  • the sealants 236 and 238 preferably have or consist entirely of polytetrafluoroethylene (PTFE).
  • a mounting device 240 is provided at its end opposite the annular piston 234, by means of which the spring 202 according to the invention can be connected to various connecting elements that are specific to the application. Furthermore, on the Closing element 212 such a connecting device can be provided.
  • the outer tube 208 of the hydraulic three-tube tension spring according to the invention is arranged concentrically with the two inner tubes 204 and 206 by means of the closing element 212.
  • the outer tube 208 is preferably connected to the connecting element 212 by friction welding.
  • a stripping device 242 is provided, with which dirt particles which are attached or adhered to the center tube 206 can be stripped off.
  • the wiping device 242 also has a device 244 against the penetration of fine dirt particles or liquids.
  • This means 244 is preferably a sealant such as e.g. an o-ring or felt ring.
  • At least one further device 246 or 248 against the ingress of dirt and liquids is preferably provided on the annular piston 234 and on the closure device 214 in order to ensure the operability of the hydraulic tension spring 202 according to the invention.
  • the arrangement of the outer tube 208 with the stripping device 242 and the devices 244, 246 and 248 ensures that the hydraulic tension spring 202 according to the invention is protected against contamination on all sliding surfaces, so that it can be used even in dirty or heavily soiled systems and nevertheless has a long service life.
  • an oil pan 250 provided on the outer tube 208 is also preferably provided in order to catch any hydraulic fluid that may escape and thus keep the environment clean.
  • at least one through hole 252 is provided in the outer tube 208.
  • the two volume spaces 224 and 232 are acted upon by a hydraulic fluid under the same system pressure via the oil fill opening or the oil fill valve 216. Due to the system pressure, the annular piston 234 and thus the central tube 206 representing the piston rod are brought into a retracted basic position. If the piston rod 206 is pulled out, the annular piston 234 moves in the direction of the control device 230 and thus reduces the volume of the second volume space 232. As a result, the hydraulic fluid flows from the second volume space 234 through the control device 230 into the first volume space 224 and displaces the piston 220 the spring force of the spring element 226 due to its incompressibility.
  • the applied movement work is stored by the prestressing of the spring means 226, so that when the piston rod 208 is relieved, the hydraulic fluid is conveyed back from the now decreasing first volume space 224 into the second volume space 232.
  • the dimensioning of the control device 230 maintains a precisely defined insertion speed.
  • the control device 230 can be designed in such a way that it does not represent too high a flow resistance in order to avoid heating, i.e. the control device 230 should at least in such a case have one, but preferably a plurality of fluid transition bores or openings with a relatively large diameter.
  • the length of the space containing the spring means can also be varied by means of an axially adjustable piston according to the explanations corresponding to FIG. 6.
  • hydraulic spring element has been shown as a hydraulic tension spring, the basic principles explained above also apply to a hydraulic compression spring using a multi-tube arrangement.
  • the piston 220 is sealed in a fluid-tight manner in the inner tube 204 by a groove-ring collar 254 and is preferably guided by a guide and sealing element 256.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne une amélioration apportée à un élément ressort, notamment un ressort à gaz ou un ressort hydraulique. L'invention est caractérisée en ce que l'élément ressort est conçu sous la forme d'un ressort à tubes multiples. Pour réaliser le ressort de l'invention, il est prévu au moins deux tubes (4, 6) placés de façon pratiquement concentrique. Au moins deux des tubes définissent au moins deux volumes (22, 24) pouvant communiquer l'un avec l'autre au moyen d'une unité de commande (20).
PCT/EP1998/008188 1997-12-18 1998-12-14 Element ressort WO1999032799A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU19682/99A AU1968299A (en) 1997-12-18 1998-12-14 Spring element
DE19881964T DE19881964D2 (de) 1997-12-18 1998-12-14 Federelement
EP98964516A EP1040282A1 (fr) 1997-12-18 1998-12-14 Element ressort
DE29880118U DE29880118U1 (de) 1997-12-18 1998-12-14 Federelement

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE1997156557 DE19756557A1 (de) 1997-12-18 1997-12-18 Gasfeder
DE19756557.3 1997-12-18
DE19846304 1998-10-08
DE19846304.9 1998-10-08
DE19848262.0 1998-10-20
DE19848262 1998-10-20

Publications (1)

Publication Number Publication Date
WO1999032799A1 true WO1999032799A1 (fr) 1999-07-01

Family

ID=27218033

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/008188 WO1999032799A1 (fr) 1997-12-18 1998-12-14 Element ressort

Country Status (4)

Country Link
EP (1) EP1040282A1 (fr)
AU (1) AU1968299A (fr)
DE (2) DE29880118U1 (fr)
WO (1) WO1999032799A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010145650A1 (fr) * 2009-06-15 2010-12-23 Manfred Endrich Amortisseur
DE102008053199B4 (de) * 2008-10-24 2011-07-07 Stabilus GmbH, 56070 Gasfeder
CN111288105A (zh) * 2020-02-20 2020-06-16 唐山保靓汽车配件有限公司 一种多通道减震器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006056666A1 (de) * 2006-06-23 2007-12-27 Krautkrämer, Hermann (verstorben) Gasdruckfeder

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2275462A (en) * 1938-02-03 1942-03-10 Arthur R Parilia Fluid spring
DE6600529U (de) * 1966-04-27 1969-01-23 Stabilus Gmbh Gasfeder zur Herstellung des Gleichgewichtes bei höhen- und neigungsverstellbaren Gegenständen
DE6946812U (de) * 1969-12-03 1970-08-13 Bauer Fritz Gasfeder mit einer durch das verhaeltnis zweier durchmesser bestimmten federkonstanten.
US3693767A (en) * 1970-11-05 1972-09-26 Hydraulic Products Corp Adjustable hydraulic shock absorber
DE2816761A1 (de) * 1978-04-18 1979-10-31 Fritz R Stolberg Pneumatische feder
DE3239254A1 (de) * 1981-10-28 1983-07-28 Elio Godega S.Urbano Treviso Pagotto Gasfeder
DE9108442U1 (de) * 1991-06-14 1991-12-05 Grobe, Herbert, 4690 Herne Gaszugfeder
EP0602917A1 (fr) * 1992-12-15 1994-06-22 Camloc (U.K.) Limited Support avec moyen de friction réglable
DE4337931A1 (de) * 1993-11-06 1995-05-11 Guenther Hahn Gaszugfeder

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2275462A (en) * 1938-02-03 1942-03-10 Arthur R Parilia Fluid spring
DE6600529U (de) * 1966-04-27 1969-01-23 Stabilus Gmbh Gasfeder zur Herstellung des Gleichgewichtes bei höhen- und neigungsverstellbaren Gegenständen
DE6946812U (de) * 1969-12-03 1970-08-13 Bauer Fritz Gasfeder mit einer durch das verhaeltnis zweier durchmesser bestimmten federkonstanten.
US3693767A (en) * 1970-11-05 1972-09-26 Hydraulic Products Corp Adjustable hydraulic shock absorber
DE2816761A1 (de) * 1978-04-18 1979-10-31 Fritz R Stolberg Pneumatische feder
DE3239254A1 (de) * 1981-10-28 1983-07-28 Elio Godega S.Urbano Treviso Pagotto Gasfeder
DE9108442U1 (de) * 1991-06-14 1991-12-05 Grobe, Herbert, 4690 Herne Gaszugfeder
EP0602917A1 (fr) * 1992-12-15 1994-06-22 Camloc (U.K.) Limited Support avec moyen de friction réglable
DE4337931A1 (de) * 1993-11-06 1995-05-11 Guenther Hahn Gaszugfeder

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008053199B4 (de) * 2008-10-24 2011-07-07 Stabilus GmbH, 56070 Gasfeder
WO2010145650A1 (fr) * 2009-06-15 2010-12-23 Manfred Endrich Amortisseur
CN111288105A (zh) * 2020-02-20 2020-06-16 唐山保靓汽车配件有限公司 一种多通道减震器

Also Published As

Publication number Publication date
DE19881964D2 (de) 2001-06-21
DE29880118U1 (de) 2001-03-22
AU1968299A (en) 1999-07-12
EP1040282A1 (fr) 2000-10-04

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