EP2428482B1 - Hebebühne für Kraftfahrzeuge - Google Patents

Hebebühne für Kraftfahrzeuge Download PDF

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Publication number
EP2428482B1
EP2428482B1 EP11007340.0A EP11007340A EP2428482B1 EP 2428482 B1 EP2428482 B1 EP 2428482B1 EP 11007340 A EP11007340 A EP 11007340A EP 2428482 B1 EP2428482 B1 EP 2428482B1
Authority
EP
European Patent Office
Prior art keywords
unit
cylinder
piston
channel
overflow
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP11007340.0A
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German (de)
English (en)
French (fr)
Other versions
EP2428482A1 (de
Inventor
Hans Nussbaum
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Otto Nussbaum GmbH and Co KG
Original Assignee
Otto Nussbaum GmbH and Co KG
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Publication date
Application filed by Otto Nussbaum GmbH and Co KG filed Critical Otto Nussbaum GmbH and Co KG
Publication of EP2428482A1 publication Critical patent/EP2428482A1/de
Application granted granted Critical
Publication of EP2428482B1 publication Critical patent/EP2428482B1/de
Active legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F7/00—Lifting frames, e.g. for lifting vehicles; Platform lifts
    • B66F7/10—Lifting frames, e.g. for lifting vehicles; Platform lifts with platforms supported directly by jacks
    • B66F7/16—Lifting frames, e.g. for lifting vehicles; Platform lifts with platforms supported directly by jacks by one or more hydraulic or pneumatic jacks
    • B66F7/20—Lifting frames, e.g. for lifting vehicles; Platform lifts with platforms supported directly by jacks by one or more hydraulic or pneumatic jacks by several jacks with means for maintaining the platforms horizontal during movement

Definitions

  • the invention relates to a lifting platform for motor vehicles according to the preamble of claim 1.
  • lifting platforms which comprise at least a first and a second lifting element, each with a hydraulic cylinder / piston unit for lifting the motor vehicle.
  • hydraulic fluid such as hydraulic oil is supplied to each cylinder / piston unit via an inlet and the hydraulic fluid displaced by the piston is discharged via an overflow.
  • the aggregates It is known to form the aggregates as a command sequence system.
  • the first cylinder / piston unit is designed as a command unit by the overflow is fluid-conductively connected to the inlet of the second-cylinder / piston unit designed as a sequence aggregate.
  • Such lifts are known in numerous embodiments.
  • the lifting elements are also known to form the lifting elements as lifting columns, wherein at least one lifting column is arranged on one side and a second lifting column on the opposite side of the vehicle.
  • the formation of the lift is known as a scissor lift, in which the lifting elements are each designed as a scissor lift.
  • the use of at least two cylinder / piston units in a command-following system has a susceptibility to errors such that due to thermal expansion and / or air bubbles in the hydraulic system, the synchronization between command and following unit may be disturbed, so that an inclined position the lift can arise in particular in the raised state and / or pressure peaks in parts of the hydraulic system.
  • the present invention is therefore based on the object to improve the known lifts, in particular with regard to the error rate of leveling the lift in the extended state and pressure peaks within the hydraulic system, for example due to inhomogeneous thermal loading of the hydraulic system and / or air connections.
  • Another object is to simplify the filling and / or venting of the hydraulic system of the lift with hydraulic fluid.
  • the lift according to the invention for motor vehicles comprises at least a first and a second lifting element, each with at least one hydraulic cylinder / piston unit for lifting the motor vehicle.
  • Each cylinder / piston unit has an inlet for supplying and an overflow for discharging hydraulic fluid in each case when lifting the motor vehicle.
  • the said units are designed as a command sequence system:
  • the first cylinder / piston unit is designed as a command unit by the overflow is fluidly connected to the inlet of the sequence unit second cylinder / piston unit connected.
  • the overflow channel is arranged and designed such that only in the region of the end position with the vehicle maximally raised or maximally lowered, the inlet of this unit is fluid-conductively connected to the overflow channel.
  • the overflow channel can either be formed integrally with a recess on the inside of the cylinder, wherein the recess is arranged in the region in which the piston is in the end position at maximum raised vehicle, or the overflow can be formed as a bypass channel, the first and has a second bore, which are spaced from each other within the cylinder wall in the direction of displacement of the piston and fluidly connected to each other.
  • both an overflow of the aforementioned arrangement and training for the end position at maximum raised vehicle and an overflow for the end position is provided at maximum lowered vehicle.
  • an overflow channel in the region of the end position with the vehicle raised to the maximum is advantageous, since here in this end position a leveling is carried out in the raised state and thus in particular measurements can be carried out with a higher accuracy due to the leveling with a maximum of the lifted vehicle.
  • At least the following unit has an overflow channel, which is fluid-conductively connected to a container for hydraulic fluid and / or to the inlet of a further cylinder / piston unit designed as a sequence unit.
  • the command unit has an overflow channel which is fluid-conductively connected to the inlet of the sequence unit. If due to a maladjustment between command and following unit, for example, as mentioned above due to thermal expansion, the command unit is already in the end position, although the follow-up unit is not yet in the end position, it results in those known from the prior art Lifting platforms an inclined position, as the following unit can not be moved to the end position. In the aforementioned preferred embodiment of the lift according to the invention, however, can be performed in the end position of the command unit hydraulic fluid from the inlet of the command unit via the overflow of the command unit to the inlet of the sequence unit, so that even in the previously described misalignment the follower unit is brought into the final position. As a result, the aforementioned inclined position of the lift is avoided.
  • both command aggregate and follow-up aggregate each have an overflow channel, wherein the overflow channel of the command aggregate with the inlet of the sequence unit and the Overflow of the sequence unit with a container and / or the inlet of another sequence unit are fluidly connected.
  • the overflow of the unit is at least in the aforementioned end position fluidly connected to the overflow of this unit.
  • the overflow is arranged and designed such that from a stroke of less than 2 cm before the end position to the end position of the inlet of the unit is fluidly connected to the overflow channel, preferably from a stroke of less than 1 cm before setting, preferably less than 0.5 cm before end position. This ensures that there is essentially a pressure and force distribution in the lifting process as in previously known lifts with known units and only shortly before reaching the end position hydraulic fluid is discharged via the overflow.
  • the overflow channel is arranged in such a way that the inlet is fluid-conductively connected to the overflow channel when the vehicle is maximally raised, there are basically no special requirements for the dimensioning between overflow channel and cylinder or piston of the unit, since in principle at maximum raised vehicle, a so-called "floating position" of the piston is possible.
  • the overflow channel such that, when the vehicle is maximally lowered, the inlet of the unit is fluid-conductively connected to the overflow channel, when the vehicle is lifted in a small initial stroke range, a portion of the hydraulic fluid flows past the piston of the cylinder via the overflow channel into the overflow of the cylinder.
  • the pump and cylinder must be designed such that the delivery volume of the pump for supplying hydraulic fluid into the inlet of the unit when lifting the vehicle is greater than the volume flowing through the overflow channel.
  • An arranged in the end position at maximum lowered vehicle overflow thus fulfills the additional task of a start-up control, d. H. that at a continuous delivery volume via the inlet of the unit initially a slowed stroke speed due to the flowing over the overflow hydraulic fluid is present and then the higher stroke speed is achieved without bypassing the piston via the overflow.
  • the overflow channel is preferably formed - apart from the cooperation of the piston of the cylinder - without moving parts. This results in a cost-effective and robust design.
  • the overflow channel is preferably formed without interposed valves, in particular without mechanically actuated valves.
  • the overflow channel comprising a recess is formed on the inside of the cylinder, wherein the recess is arranged in the region in which the piston is in the end position with the vehicle raised to the maximum.
  • the overflow channel comprises a groove on the inside of the cylinder.
  • Typical hydraulic cylinders have a cylinder head in the region of the end position of the piston.
  • the overflow channel of the unit is at least partially formed in the cylinder head of the cylinder of this unit. This results in a particularly robust embodiment, since no separate line paths for forming the overflow are necessary.
  • the overflow channel preferably comprises a groove on the inside of the cylinder and a groove in the bottom region of the cylinder head, which preferably opens into the overflow channel.
  • hydraulic cylinders are designed such that in the end position the piston does not lie flush against the bottom of the cylinder head, for example because the piston rod projects beyond the piston.
  • the aforementioned groove in the cylinder bottom is not absolutely necessary for the formation of the overflow.
  • the overflow channel of the unit is designed as a bypass channel and arranged such that in the end position, a fluid-conducting connection between inlet and overflow of this unit consists, without flow contact between the flowing through the overflow hydraulic fluid and the piston seal of the piston.
  • This preferred embodiment is based on the Applicant's knowledge that the risk of damaging or at least impairing the sealing effect of the piston seal of the piston exists when the hydraulic fluid flows along the piston seal with an abrasive effect when flowing through the overflow channel. This is due in particular to partly high pressure and flow rate, which have a negative effect on the material of the piston seal.
  • the overflow channel is designed in the form of a bypass channel, so that although inlet and overflow of the unit are fluid-conductively connected through the bypass channel, the hydraulic fluid does not come into contact with the piston seal when flowing through the bypass channel, but in a separate Channel flows around.
  • the overflow channel is in each case fluid-conductively connected at the ends via an opening in the cylinder wall, preferably via a bore to the cylinder space.
  • a particularly structurally simple embodiment results in this case, in which two spaced apart in the direction of displacement of the piston bores in the cylinder wall are provided, which bores, preferably within the cylinder wall, are fluid-conductively interconnected to form the bypass channel.
  • the raising and lowering of the lift is controlled by means of a control unit and this is preferably designed such that at certain predeterminable time intervals, or depending on measured values of an outside temperature sensor and / or pressure sensor the user is suggested a method in the end position, if the end position for a predetermined time range and / or after exceeding a predetermined outside temperature difference and / or external pressure change was not approached.
  • the lift according to the invention is particularly suitable for use in the repair and / or maintenance of motor vehicles. Likewise, it can be used advantageously in parking systems, in particular in parking systems in which motor vehicles are parked one above the other in double or multiple parking systems.
  • the lift of the embodiment shown in the figures is designed as a lifting column lift 1, with two lifting columns 1 a and 1 b formed lifting elements.
  • Each lifting column has a movable up and down Supporting shears (2a, 2b), which engage under operation between the lifting columns 1 a, 1 b arranged motor vehicle so that it can be raised by raising the support shears 2a and 2b.
  • the control is carried out by means of a unit 3, which comprises a control panel, not shown, for operation by a user.
  • the lifting column 1 a comprises a first hydraulic cylinder / piston unit for raising and lowering the supporting shears 2 a and accordingly comprises the lifting column 1 b, a second cylinder / piston unit for raising and lowering the supporting shears 2 b.
  • the first unit of the lifting column 1 a is formed as a command aggregate, by the overflow of the first unit is fluidly connected by means of a first overflow line 4 with the inlet of the second unit formed as a sequence aggregate. Both units are designed such that in the end position of the piston maximally raised support scissors are present.
  • the units 9 and 10 are arranged in the lifting columns 1 a and 1 b respectively in the upper region and the pistons are connected to the respective supporting shears 2 a and 2 b, so that a raising of the pistons 9 b and 10 b causes a lifting of the supporting shears 2 a and 2 b.
  • hydraulic oil is supplied by switching a 2/2-way valve 12 via a return line 13 to the tank 5, wherein the speed of lowering via a lowering brake 14 is controllable.
  • a line with an interposed pressure limiting valve 15 is arranged between the first supply line 8 and the return line 13.
  • the first cylinder / piston unit has an overflow channel 9c and the second cylinder / piston unit 10 has an overflow channel 10c. These are each arranged in the end region of the cylinder by the pistons 9b and 10b are at maximum raised support shears 2a and 2b.
  • the overflow channel 9 c is fluid-conducting with the first overflow line 4 and the overflow channel 10 c is fluid-conductively connected to the second overflow line 11.
  • the inlet 9a is fluid-conductively connected to the first overflow line 4 via the overflow channel 9c.
  • the inlet 10a is fluid-conductively connected to the second overflow line 11 via the overflow channel 10c, provided that the piston 10b is in the end position.
  • the lift 1 can be easily filled with hydraulic oil and vented.
  • hydraulic oil flows via the overflow channel 9c and the first overflow line 4 to the inlet 10a and thus to the second unit 10.
  • hydraulic oil flows via the overflow channel 10c and the second overflow line 11 back to tank 5. In this way, the hydraulic system is filled with hydraulic oil and vented in a simple manner.
  • FIG. 3 is a partial section of the cylinder / piston unit 9 according to sign A in FIG. 2 represented, with the piston 9b in contrast to FIG. 2 in end position.
  • FIG. 3 represents a sectional view parallel to the central axis of the piston 9b and the cylinder 9d of the cylinder / piston unit 9, wherein the section extends through the central axis.
  • the cylinder 9d has a cylinder head 9e by forming an overflow port 9f. This is fluidly connected to the first overflow line 4.
  • This overflow channel 9c comprises a groove 9g formed in the cylinder 9d in the region B, which groove extends over a certain stroke length approximately to the cylinder end.
  • the piston 9b has a seal 9h in the form of an O-ring which, except in the end position, seals the piston 9b with respect to the inner wall of the cylinder 9d.
  • a seal 9h in the form of an O-ring which, except in the end position, seals the piston 9b with respect to the inner wall of the cylinder 9d.
  • the interior of the cylinder 9d according to the dashed arrow in FIG. 3 fluidly connected to the groove 9g.
  • the groove 9g opens into a (not shown) recess in the cylinder head 9e, which in turn opens into the overflow port 9f.
  • piston 9b In the end position of the piston 9b according to FIG. 3 Thus, there is a fluid-conducting connection of the interior of the cylinder 9d via the groove 9g to the overflow port 9f, so that the inlet of the unit 9 is fluidly connected to the overflow port 9f and thus the first overflow line 4.
  • piston 9b On the other hand, piston 9b is located outside the end position, so that the seal 9h rests against the inner wall of the cylinder 9d over the entire circumference, there is no fluid-conducting connection between inlet and overflow of the unit 9.
  • FIG. 4 time a partial section of another embodiment of a cylinder / piston unit 9 ', for use in a lift according to FIG. 1 ,
  • the piston 9b ' is in the selected representation in the lower end position, ie at maximum lowered vehicle.
  • FIG. 4 also represents an axial section of the cylinder / piston unit 9 '.
  • the cylinder 9d ' has a cylinder head 9e' by forming an overflow port 9f '. This is when using this unit in the lift according to FIG. 1 connected to the overflow line 4.
  • the cylinder 9d ' has a first overflow channel 9c', which analogous to the overflow channel 9c according to FIG. 3 is formed and an analogous groove 9 g 'comprises, which is formed on the inside of the cylinder 9 d'.
  • this exemplary embodiment of the cylinder / piston assembly 9 ' has a second overflow channel which comprises a second groove 9 g. "This groove 9 g" is likewise formed on the inside of the cylinder 9d' and extends at least over the height of the piston 9b '. , in FIG.
  • the cylinder / KolbenAg gregates 9 'in the lower end position of the piston 9b', ie at maximum lowered vehicle, for example, a filling of the hydraulic system possible because hydraulic fluid starting from the inlet 9a 'via the groove 9g "the piston 9b 'and can flow to the overflow 9f' and thus the hydraulic system can be filled and / or vented FIG. 4 always a lowering to the end position, so that in this case, even in the lowered state, a leveling takes place and any misalignments due to thermal expansion are compensated.
  • partial image 5a shows an axial sectional image
  • partial image 5b shows a detail enlargement of region Z according to partial image 5a
  • partial image 5c again shows a partial enlargement of region Y according to partial image 5b.
  • FIG. 6 shows a partial section of a cylinder 9d ", in the cylinder wall by means of a plurality of bores as a bypass channel 9c" formed overflow channel is shown.
  • partial image 6b represents a partial enlargement of the partial image 6a in the area of the bypass channel 9c ".
  • a first bore 16a and a second bore 16b are provided in a cylinder wall of the cylinder 9d "The bores 16a and 16b respectively open into a third bore 16c which has a larger diameter compared to the first and second bores.
  • the third bore 16 c is formed by means of a closure cap 17 against the environment fluid-tight.
  • a closure cap 17 against the environment fluid-tight.
  • the closure lid 17 is not shown.
  • the closure lid 17 has an annular recess 17a on its side facing the piston. Starting from the mouth of the first bore 16a into the cylinder chamber, there is thus a fluid-conducting connection via the mouth of the first bore 16a into the annular recess 17a of the closure cap 17.
  • the annular recess 17a is in turn fluid-conductively connected fluid-conductively to an opening of the second bore 16b facing it , which second bore 16b in turn opens into the cylinder space.
  • the holes 16a and 16b have approximately a diameter of 1 mm.
  • the bore 16c has approximately a diameter of 9 mm.
  • the centers of the bores 16a and 16b are spaced about 6 mm apart.
  • the closure lid 17 is arranged by means of fastening elements 17b on the cylinder wall of the cylinder 9d ".
  • the unit 9 has the advantage that when overflow of the piston seal 9h" via the bypass channel 9c "no wear and / or damage to the piston seal 9h" takes place.
  • a slotted guide ring 22 is arranged, which allows a vertical flow of oil between the piston and the cylinder wall due to the slot.
  • FIG. 7 shows a further embodiment of a cylinder / piston unit 9 "', which is designed as a per se known synchronous telescopic cylinder / piston unit.
  • the unit 9'" thus has two concentrically arranged pistons 9b “'. 1 and 9b"' 2 and two concentrically arranged cylinders 9d “'. 1 and 9d”' 2 on.
  • the piston rod of the piston 9b “'. 1 thus forms the cylinder 9d"'. 2 of the second cylinder / piston unit.

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Types And Forms Of Lifts (AREA)
  • Forklifts And Lifting Vehicles (AREA)
EP11007340.0A 2010-09-14 2011-09-08 Hebebühne für Kraftfahrzeuge Active EP2428482B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010045287A DE102010045287A1 (de) 2010-09-14 2010-09-14 Hebebühne für Kraftfahrzeuge

Publications (2)

Publication Number Publication Date
EP2428482A1 EP2428482A1 (de) 2012-03-14
EP2428482B1 true EP2428482B1 (de) 2014-11-19

Family

ID=44653955

Family Applications (1)

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EP11007340.0A Active EP2428482B1 (de) 2010-09-14 2011-09-08 Hebebühne für Kraftfahrzeuge

Country Status (7)

Country Link
US (1) US9637364B2 (ru)
EP (1) EP2428482B1 (ru)
JP (1) JP5881144B2 (ru)
CN (1) CN102398874B (ru)
BR (1) BRPI1104755A2 (ru)
DE (1) DE102010045287A1 (ru)
RU (1) RU2577440C2 (ru)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102016114727A1 (de) * 2016-08-09 2018-02-15 ATH-Heinl GmbH & Co. KG Gleichlaufsteuerung für ein Hydraulikzylindersystem

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US9463962B2 (en) 2013-03-13 2016-10-11 Mi-Jack Products, Inc. Dynamic sensor system and method for using the same
US9266690B2 (en) 2013-03-13 2016-02-23 Mi-Jack Products, Inc. Light positioning system and method of using the same
CN104006027A (zh) * 2013-05-22 2014-08-27 芜湖高昌液压机电技术有限公司 汽车举升机串联同步油缸自动排气和调平
NL2011132C2 (en) 2013-07-10 2015-01-13 Stertil Bv Lifting system for lifting a vehicle and method for operating the lifting system.
DE102013221211A1 (de) 2013-10-18 2015-04-23 Jürgen Holzhäuser Vorrichtung und Verfahren zum Bewegen eines Transportelements eines Last- oder Personenaufzugs
DE102013019722A1 (de) 2013-11-27 2015-05-28 Otto Nussbaum Gmbh & Co. Kg Hubvorrichtung zum Heben schwerer Lasten
DE102014113301A1 (de) 2014-09-16 2016-03-17 Otto Nussbaum Gmbh & Co. Kg Hebebühne mit Rücklaufsperre
EP3064782B1 (de) * 2015-03-06 2018-06-20 Otto Nussbaum GmbH & Co. KG Zylinderkolbenaggregat
US10106378B2 (en) 2015-11-03 2018-10-23 General Electric Company System and method for lifting with load moving machine
US10858054B2 (en) 2018-01-31 2020-12-08 Honda Motor Co., Ltd. Multi-stage shift pack assembly and method
CN108317115B (zh) * 2018-04-09 2023-08-04 中山市颉榕汽车维修检测设备有限公司 剪式举升机调平装置、举升系统及剪式举升机
IT201900006900A1 (it) 2019-05-16 2020-11-16 O Me R Spa Dispositivo a colonna per il sollevamento di un carico.
IT202000006085A1 (it) 2020-03-23 2021-09-23 O Me R Spa Braccio per una struttura di supporto di un carico
DE102022122724A1 (de) 2022-09-07 2024-03-07 Nussbaum Automotive Lifts Gmbh Hydraulikaggregat mit Überströmkanal und Hubvorrichtung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016114727A1 (de) * 2016-08-09 2018-02-15 ATH-Heinl GmbH & Co. KG Gleichlaufsteuerung für ein Hydraulikzylindersystem
DE102016114727B4 (de) * 2016-08-09 2021-02-11 ATH-Heinl GmbH & Co. KG Verfahren zur Gleichlaufsteuerung eines Hydraulikzylindersystems sowie Mehrsäulen-Fahrzeughebebühne

Also Published As

Publication number Publication date
RU2011137212A (ru) 2013-03-20
CN102398874A (zh) 2012-04-04
US20120067672A1 (en) 2012-03-22
RU2577440C2 (ru) 2016-03-20
JP2012062199A (ja) 2012-03-29
US9637364B2 (en) 2017-05-02
DE102010045287A1 (de) 2012-03-15
CN102398874B (zh) 2015-06-03
JP5881144B2 (ja) 2016-03-09
EP2428482A1 (de) 2012-03-14
BRPI1104755A2 (pt) 2015-07-14

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