Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
  • F15B15/20—Other details, e.g. assembly with regulating devices
  • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
  • F15B15/222—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which throttles the main fluid outlet as the piston approaches its end position
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
  • F15B15/20—Other details, e.g. assembly with regulating devices
  • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
  • F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position

Definitions

• the present invention relates to a pneumatic cylinder with end position damping with a housing in which at least one push rod element with at least one sealing element is mounted so as to be linearly movable, the push rod element being assigned at least one damper sleeve which engages in the end positions in end-side bearing elements, and a damper sleeve or its bearing.
• Pneumatic cylinders of this type are known and customary in the most varied of forms and designs on the market. They essentially serve to move any objects and are often used in handling technology today.
• a push rod element can be moved in a piston-like manner within a housing, the push rod element being mounted such that it can be moved back and forth via end-side bearing elements.
• End position damping is particularly problematic since throttle valves or the like have been used in the end bearing elements to dampen the corresponding end positions when the push rod element, in particular its damper sleeve, enters a corresponding mounting of the bearing elements.
• a further disadvantage is that with conventional throttles or throttle valves, in particular with large mass differences which are present on the push rod element of a pneumatic cylinder, vibrations occur in the end position area. Furthermore, conventional cylinders can only be used to a very limited extent, which relates in particular to the absorption of loads of different sizes and also high speeds and / or accelerations.
• the present invention has for its object to provide a pneumatic cylinder of the type mentioned, with which the disadvantages mentioned are eliminated and with which, in particular, end position damping is to be substantially improved, additional manufacturing costs being eliminated and readjustment by cost-intensive specialist personnel being eliminated. In addition, higher cycle times should be possible with constant end position damping. Initial installation and immediate operation should be possible without specialist personnel and without adjusting a limit position.
• the damper sleeve or its bearing has at least one notch for end position damping and venting.
• a notch is preferably provided in an outer lateral surface of a damper sleeve or in an inner lateral surface of a bearing of the damper sleeve, which notch extends in the axial direction of the bearing or the damper sleeve.
• the pressure built up in the interior of the housing can be released in a throttle-like manner for end position damping. This dampens a movement of the push rod element in the end position. It has proven to be particularly advantageous to provide the notch discontinuously in the outer surface of the damper sleeve or in its storage.
• the notch is formed deeper on one end face, near a phase of the damper sleeve, than on its other end face, where it almost overflows into the outer surface and runs out into it. The same applies to the storage, should the notch be provided in the storage.
• the notch can be triangular, quadrangular, arched or of a different cross-sectional shape.
• a plurality of indentations are also intended either to be assigned to the damper sleeve in its jacket surface, or to be provided in an inner jacket surface of the mounting of damper sleeves.
• the notches are preferably provided axially and linearly parallel to the push rod or parallel to the push rod element. However, these can also be provided, for example, diagonally or in a serpentine manner in the lateral surface in the longitudinal direction. However, the present invention should not be limited to this.
• a pressure relief valve is additionally provided in a pneumatic cylinder, in particular in the case of its bearing elements, which is connected to a Compression space, which is formed between the sealing element, damper sleeve, inner surface of the housing and an end face of the bearing elements, is connected.
• the rapid acceleration or movement of the push rod element against the end face of the bearing element increases a pressure which, although it can expand in the above-described manner via the at least one notch in a cavity of the bearing element, can be used to prevent vibrations, in particular when damping end positions
• Reduce pressure peaks that occur via at least one pressure relief valve which is preferably connected to an environment or a cavity of the bearing elements by means of a bypass. Only the pressure peaks are damped by preferably opening the pressure relief valve for a short time.
• Figure 1 is a schematic plan view of a pneumatic cylinder with inserted push rod element
• Figure 2 is a schematic plan view of a push rod element with two damper sleeves and sealing elements mounted between them and a partial longitudinal section through a bearing element with storage for receiving the damping sleeve;
• FIG. 3 shows a longitudinal section through a damper sleeve according to the invention
• FIG. 4 shows a side view of the damper sleeve according to FIG. 3;
• FIG. 5 shows a longitudinal section through a further exemplary embodiment of the damper sleeve according to FIG. 3;
• FIG. 6 shows a side view of the damper sleeve according to FIG. 5;
• FIGS. 7a and 7b schematically illustrated side views of a damper sleeve with notch according to the invention
• FIGS. 8a and 8b are side views of the damper sleeve according to FIGS. 3, 5 and 7a as further exemplary embodiments with a notch according to the invention;
• FIG. 9 shows a schematically illustrated longitudinal section through the damper sleeve according to FIG. 7a along line IX-IX;
• FIG. 10 shows a schematically illustrated top view of a possible further arrangement of the notch in a lateral surface of a damper sleeve
• FIG. 11 shows a schematically illustrated longitudinal section through a further exemplary embodiment of the damper sleeve
• FIG. 12 shows a side view of the damper sleeve according to FIG. 11;
• FIG. 13 shows a schematically illustrated top view of the further exemplary embodiment of the damper sleeve according to FIGS. 11 and 12;
• FIG. 14 shows a schematically illustrated partial longitudinal section through a further exemplary embodiment of a pneumatic cylinder according to FIG. 1.
• a pneumatic cylinder R has a housing 1 which is cylindrical in the interior.
• Bearing elements 2.1, 2.2 are connected at the ends to the housing 1, which act on the one hand to apply pressure to an internal push rod element 3 for moving any loads back and forth and to control them accordingly.
• Corresponding openings 4.1, 4.2 are provided in the bearing elements 2.1, 2.2, which form the corresponding connections for the pneumatic lines (not shown here) for supplying air or gas into the interior of the housing 1. If air is introduced into the housing 1 through the opening 4.1 via the bearing element 2.1, the push rod element 3 can be moved in the direction of the bearing element 2.2. If, on the other hand, air or gas is introduced into the housing 1 via the opening 4.2, the push rod element 3 can be moved back.
• sealing elements or the like are provided in the bearing elements 2.1, 2.2, in which corresponding damper sleeves 5, which are assigned to the push rod element 3, as shown, for example, in FIG. 2, engage. At least one sealing element 6 is provided between the two damper sleeves 5, which runs like a piston within the cylindrical housing 1 and supports the push rod element 3 on the one hand and seals on the other hand.
• the diameter of the damper sleeve 5 is somewhat larger than that of the push rod 7 of the push rod element 3.
• the damper sleeves 5 engage in the corresponding bearing elements 2.1, 2.2, in particular in their bearing 13 in a sealed manner, the opening 4 being closed.
• the compressed air for damping a pushing movement of the push rod element 3 is continuously and slowly discharged via a throttle, a throttle valve or the like in an end position.
• corresponding throttle elements can be dispensed with, in which, according to the invention, the damper sleeve 5 or its bearing 13 is provided with at least one notch 8 in the lateral surfaces 9 thereof. As shown in particular in FIG. 2, the notch 8 is provided linearly and parallel to the push rod 7 in a longitudinal direction of the damper sleeve 5.
• the push rod element 3 in particular the damper sleeve 5 gets into the corresponding seal of the bearing elements 2.1 or 2.2 or into the bearing 13 in the respective end positions, then the compressed air in the bearing element 2.1 or 2.2 or in the end element can dampen the movement of the push rod element 3 Storage 13 continuously, permanently and slowly escape via the notch 8.
• the damper sleeve 5 is provided with a phase 10, which is used for insertion into the bearing 13 of the bearing elements 2.1, 2.2.
• FIGS. 3 and 5 each show longitudinal sections of the damper sleeve, in which the notch 8 can be seen.
• the notch 8 is triangular in cross section.
• the notch 8 is recessed in the area of an end face 11, starting much deeper from the outer surface 9 and, viewed from the outer surface 9, is tapered to the opposite end side 12.
• the notch 8 is very small or almost merges into the outer surface 9.
• a cross-sectional area of the notch 8 changes permanently, starting from the end face 11, this cross-sectional area tapering in the direction of the end face 12.
• a notch 8 described above can be provided for a bearing 13 of the bearing elements 2.1 or 2.2 in the region of an inner lateral surface 9. Then, for example, a sealing ring would be provided accordingly on the damper sleeve 5, so that the pressure or air or gas can escape via the notch 8 in the inner lateral surface 9 of the bearing 13 of the bearing elements 2.1 or 2.2 for end-position damping. This should also be within the scope of the present invention.
• notch 8 is assigned to the damper sleeve 5
• corresponding sealing elements are provided within the bearing 13 of the bearing elements 2.1, 2.2. If the at least one notch 8 is provided within the lateral surface 9 of the bearing 13 of the bearing elements 2.1, 2.2, corresponding sealing elements are assigned to the damper sleeve 5.
• FIGS. 7a and 7b show side views of a corresponding damper sleeve 5, from which it can be seen that the notch 8 runs approximately triangularly and includes an angle ⁇ of approximately 30 to 90 °, preferably 60 °.
• an enlarged partial cross-section shows that the notch 8 has a maximum depth T in the region of the end face 11 and tapers into the plane of the lateral surface 9 towards the other opposite end face 12.
• the notch 8, viewed in an axial direction, includes an angle ⁇ of 1 ° to 3 ° and preferably 1.7 ° to 2.0 ° to the surface 9.
• the invention is not intended to be limited to these angles ⁇ .
• This change in cross section or this continuous runout of the notch 8 should also be provided in the bearing 13, as is shown in particular in FIG. 2.
• a maximum depth T should always taper from the end face 11 to the opposite end face 12.
• a top view of the damper sleeve 5 is shown, in which the notch 8 is provided, for example, diagonally in the lateral surface 9.
• the present invention is also not limited to this.
• a further damper sleeve 5.1 is shown, in the lateral surface 9 of which at least one recess 14, in particular opening, bore or blind hole, is preferably provided axially.
• the recess 14 projects into the end face 11 and leads to the end face 12.
• the recess 14 is a blind hole.
• radial bores 15 hit the recess 14 from the outside, as is also shown in the top view according to FIG. 13.
• the mode of operation of the present exemplary embodiment corresponds approximately to that described above for FIGS. 2 to 6.
• the individual bores 15 can be arranged axially at variable intervals A, in order to influence damping behavior.
• a diameter D of the individual bores 15 can also vary, so that this can influence the outflow behavior and thus also the damping behavior of the compressed gas.
• the speed of the push rod element 3 should be damped to almost zero without the sealing element 6 striking the bearing element 2.1, 2.2 at high speed.
• the air as it is shown in particular in FIGS. 2 to 10, can escape in a determinable manner via the so-called notch 8, it being advantageous that such a notch does not impair the sealing element in the bearing element 2.1, 2.2 and the air, in particular the gas can flow along the notch 8, so that self-cleaning takes place here.
• FIG. 14 a partial longitudinal section through a further exemplary embodiment of a pneumatic cylinder Ri is shown, which corresponds approximately to the type described above.
• the bearing elements 2.1, 2.2 which are provided at one end and at the other end of the pneumatic cylinder R x , are only shown on one side for the sake of simplicity.
• the housing 1 is connected to the end of the at least one bearing element 2.1, 2.2, a sealing ring 16 of a flange, not shown here, producing a seal between the housing 1 and the bearing element 2.1, 2.2.
• this has a preferably cylindrical cavity 17, the bearing 13, for example as a sealing ring or similar sealing element, being used in the region of an end face 18 of the bearing elements 2.1, 2.2.
• an overpressure channel 19 opens into the end face 18 within the housing 1, to which an overpressure valve 20 connects.
• the pressure relief valve 20 consists of a spherical element 21 which closes the channel 19, a spring element 22 and closure element 23. These are inserted into a blind hole 24 of the bearing element 2.1, 2.2.
• bypass 25 which connects a connection between the overpressure channel 19 and the cavity 17 of the bearing elements 2.1, 2.2, if an overpressure builds up inside a compression space 26, which causes the above-described escape of air via the notch 8 in the cavity 17 is not sufficient.
• the pressure relief valve 20 is actuated, the ball 21 releases a connection between the pressure relief channel 19 and the bypass 25, so that the compressed air can get into the cavity 17 and from there either be discharged into the environment or via the openings 4.1, 4.2 for supply or can escape to remove air.
• the bypass 25 preferably opens into the cavity 17 behind the bearing 13 and near the opening 4.1, 4.2.
• vibrations in the end positions are completely eliminated by relieving the pressure peaks via the pressure relief valve 20.
• a light and a very heavy weight can be moved without readjustment using one and the same pneumatic cylinder Ri, and the mass differences can be between 5 and 60 kg, preferably between 5 and 40 kg, without the need for readjustment.
• Another advantage of the present invention is that it enables end position damping to be set in pneumatic cylinders.
• the pneumatic cylinders according to the invention work in absolute Synchronous operation, whereby faster machine cycle times can be achieved.
• Another advantage is that no initial adjustment of the damping of the pneumatic cylinder is necessary. Throttling as well as throttle bores and throttles are not necessary. These often become dirty and therefore require frequent end position adjustment or re-adjustment of the machines. Overall, this leads to an increased service life of the pneumatic cylinders R, Ri.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Fluid-Damping Devices (AREA)
• Cookers (AREA)
• Diaphragms For Electromechanical Transducers (AREA)

Applications Claiming Priority (5)

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• 2001
  • 2001-05-22 EP EP01943426A patent/EP1283958B1/fr not_active Expired - Lifetime
  • 2001-05-22 US US10/296,576 patent/US20030140781A1/en not_active Abandoned
  • 2001-05-22 CA CA002410374A patent/CA2410374A1/fr not_active Abandoned
  • 2001-05-22 AT AT01943426T patent/ATE335135T1/de active
  • 2001-05-22 DE DE50110624T patent/DE50110624D1/de not_active Expired - Lifetime
  • 2001-05-22 WO PCT/EP2001/005852 patent/WO2001090585A1/fr not_active Ceased

Non-Patent Citations (1)

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