EP2719653A1 - Height adjustable lifting table that can be adjusted in a vertical direction using a motor, such as for use in car bodywork construction in the motor vehicle industry - Google Patents

Abstract

The table (1) has a frame-like underframe (3) attached to an installation bottom part. A load-bearing capacity body (2) is stroke-movably, vertical adjustably and immovably stoppable in vertical directions (A, B) and locked by swivel-movable steering wheel elements (4-7) with respect to the underframe. Multiple spaced pressure spring elements (41, 42) are supported against the load-bearing capacity body. The spring elements receive a portion of weight transferred by the load-bearing capacity body on the steering wheel elements. The pressure spring elements are designed as screwing pressure springs, leaf spring elements and steel springs.

Description

The invention relates to a motorized height-adjustable in the vertical direction lifting table, for example, for use in the bodywork of the automotive industry.

Motor driven lifting tables are already known in various constructions.

The prior art include lifting tables, the height adjustment over cylinders or spindle drives the load-carrying body relative to a frame-like base. Load-receiving body and base are connected to each other via scissor-shaped crossed link elements, wherein the scissor-type link elements are pivotally connected to each other in their possible average length range via pivot axes. In one type, for example, a pair of handlebars located at one end of the undercarriage is connected to the undercarriage pivotally coupled, while the other pair of arms is guided over rollers in rails of the undercarriage. The adjustment is made by piston-cylinder units.

Other types of handlebar elements use simple or multiply arranged handlebar elements in the manner of Nuremberg scissors, by which the load-receiving body is height adjustable relative to a frame-like base.

It is also known to arrange a plurality of such scissor-type arranged link elements in Längsachsrichtung of the undercarriage next to each other and synchronously adjust to lift the load-receiving body and lower.

Unfavorable in many types is the low tipping stability, especially when heavy loads, for example, bodies are to be moved in production lines in the automotive industry.

Hub tables are also known which have scissor-like intersecting link elements which extend between the load-receiving body and the frame-shaped subframe, with a central lifting column lifting and lowering the load-receiving body.

In the bodywork of the automotive industry, the demand is often made that such lifting tables to be moved when transporting body parts on pallet trucks to be moved in a production line, whereby the requirement is made to record each recorded load in different height ranges and at another level for removal.

Furthermore, lifting tables are known in which the load-receiving body is also adjustable by motor in the vertical direction via link elements, the motors must be correspondingly strongly dimensioned according to the particular occurring in the bodywork of the automotive industry high weights and therefore occupy a large volume below the load receiving body, so that the load-receiving body has a correspondingly small stroke, because a part of the distance between the lower frame and underside of the load-receiving body is occupied by the engine and any gear parts. Also, the engine must have a correspondingly high energy consumption, that is, develop a large torque to move the loads can. The invention has for its object to provide a height-adjustable motorized lift table in the vertical direction, which works energy efficient and is particularly suitable because of its robustness for use in the bodywork of the automotive industry.

This object is achieved by the reproduced in claim 1 features.

• Gewicht des Lastaufnahmekörpers mit Last = 1500 kg
• Hub 0 bis 600 mm = 2,0 s
• Hub 0 bis 800 mm = 2,6 s

The object is achieved by a height-adjustable motorized lift table, for example, for use in the bodywork of the automotive industry, with a ground floor associated frame-like base and a relatively liftable load-receiving body, the liftable by pivotable link elements relative to the undercarriage in the vertical direction and also immovably stoppable in the respective height adjustment and, for example, motor-lockable, in particular with two or more spaced, against the load-receiving body supporting compression spring elements which absorb a considerable part of the weight transferred from the load-receiving body and on the link elements. Such a lifting table according to the invention has the advantage that a part of the energy required to move the load-receiving body is expended by the compression springs. The following example may clarify this:

• Weight of load-carrying body with load = 1500 kg
• Stroke 0 to 600 mm = 2.0 s
• Stroke 0 to 800 mm = 2.6 s

State of the art:

Double box lifter without spring compensation requires two gear boxes each with an operating torque of 8000 Nm and a drive motor of 84 Nm.

Lifting table according to the invention:

A lifting table for the identical application, on the other hand, has two gearboxes with a drive torque of 2700 Nm per box. The drive motor only needs to transmit 26 Nm.

Due to the reduction of the transmission due to lower performance data, for example, by a height of 150 mm low compared to the prior art in a lifting table according to the invention with compression spring elements can be achieved.

The compression spring elements compensate for the stroke in the lower stroke range 100% and decrease with the lifting movement (maximum stroke 800 mm in the example assumed) to 26%.

As a result, a lifting table according to the invention also works in an environmentally friendly manner because of its low energy consumption and, in addition to saving investment costs, also brings about a not inconsiderable saving in energy costs.

Further inventive embodiments are described in claims 2 to 23 .

Claim 2 describes a lifting table, in which the compression spring elements on the one hand - even indirectly - against the underside of the load-carrying body and on the other - optionally indirectly - also supported against the underframe under resilient bias. As a result, support the compression spring elements not only from the beginning, but also with increasing stroke the drive motor.

Preferably, the compression spring elements are arranged in the space between the link elements according to claim 3 . As a result, the construction dimensions of the lifting table are not increased.

In one embodiment, the compression spring elements are arranged in the space at the end portions of the lift table between the load-receiving body and the base - claim 4. This will make room for any other transmission elements such as drive shafts and the drive motor between the link elements.

Preferably, according to claim 5, the compression spring elements are arranged in the bounded by mutually parallel boundary planes, which include the load-receiving body and the base space. This also achieves a compact construction of the lifting table.

Claim 6 describes a lifting table in which the compression spring elements are arranged asymmetrically with respect to the transverse center axis of the undercarriage, while in the embodiment according to claim 7, the compression spring elements asymmetrically with respect to the transverse center axis of the undercarriage and are arranged asymmetrically with respect to the longitudinal center axis of the lifting table. This makes it possible in the hand, depending on the available space to arrange the compression spring elements, also with regard to the load to be transported, which rests on the load-receiving body. It is also nothing in the way in case of need in each case several compression spring elements, for example, to arrange in pairs next to each other.

In contrast, in the embodiment according to claim 8, the compression spring elements arranged symmetrically with respect to the transverse center axis of the undercarriage, while in the embodiment according to claim 9, the compression spring elements on the longitudinal center axis of the undercarriage or in pairs symmetrically to this and symmetrical to the transverse center axis of the undercarriage are arranged.

Advantageously, in the embodiment according to claim 10, each compression spring element by the load-receiving body on the one hand and the base on the other hand assigned, in pairs, coaxial with each other, peg-shaped guide elements, in particular sleeves, mounted and guided, wherein the guide elements with a certain length in the respective spring element, preferably positive fit, intervene. As a result, the compression spring elements on a certain length not only held, but also safely guided in each stroke position of the load-carrying body.

This also applies to the embodiment according to claim 11, wherein the guide elements with a certain length section engage around the respective compression spring element, preferably in a form-locking manner.

According to claim 12 , the compression spring elements take over more than 10% of the total weight of the load-carrying body with the load resting on it, in particular 26% to 100%.

Claim 13 describes a lifting table, wherein the compression spring elements are designed as helical compression springs, while in the embodiment according to claim 14, the compression spring elements are designed as leaf spring elements.

Preferably, the described compression spring elements according to claim 15 made of spring steel.

A preferred embodiment of the lifting table is characterized according to claim 16, characterized in that by means of an electric drive motor via a respective propeller shaft more, for example, in the respective end region of the undercarriage arranged link elements - optionally indirectly - are driven to pivot.

A further preferred embodiment is characterized according to claim 17, characterized in that on each longitudinal side in the respective end region of the lifting table each two horizontal axes with the load receiving body pivotally coupled link elements are arranged, the rectilinear at their opposite, the subframe associated end portions via slotted guides in Längsachsrichtung of the undercarriage are guided, and that in the central longitudinal region of each link member via a horizontal pivot axis depending on a support lever is pivotally mounted, which is connected at its opposite end portion via a horizontal pivot axis also with a pivot shaft of a transmission which is driven via the associated propeller shaft.

According to claim 18 , the slotted guides on U-rails, the U-legs are each directed to the inside of the undercarriage and in which roller guides for the respective link element are guided in a straight line and stored.

In the embodiment according to claim 19 , the lifting table on a designed as a reversible electric motor drive motor, in particular an asynchronous motor or z. B. is a synchronous motor, which is preferably in the middle length range, preferably on the transverse center axis of the undercarriage, for example centrally located. This results in a compact design.

Claim 20 describes a further advantageous embodiment, which also applies to claim 21 . In the embodiment according to claim 22 , the drive motor is arranged outside the transverse center axis of the undercarriage, while the drive motor is arranged in the embodiment according to claim 23 with its longitudinal axis parallel or approximately parallel to the longitudinal center axis of the undercarriage.

Fig.1

einen Hubtisch gemäß der Erfindung, bei welchem sich der Lastaufnahmekörper in seiner maximal angehobenen oberen Stellung befindet;

Fig. 2

der aus Fig. 1 ersichtliche Hubtisch, bei dem sich der Lastaufnahmekörper in seiner maximal abgesenkten unteren Stellung befindet, und

Fig. 3

eine Draufsicht auf das rahmenförmige Untergestell mit zentralem Antriebsmotor, Gelenkwellen und Getrieben.

In the drawing, the invention - partly schematically - illustrated in one embodiment. Show it:

Fig.1

a lift table according to the invention, in which the load-receiving body is in its maximum raised upper position;

Fig. 2

the out Fig. 1 apparent lift table, in which the load-receiving body is in its maximum lowered lower position, and

Fig. 3

a plan view of the frame-shaped base with central drive motor, drive shafts and gears.

The reference numeral 1 denotes a lifting table as a whole, which essentially consists of a frame-like, upper load-receiving body 2 and a frame-like underframe 3 assigned to the erection floor, not shown.

The load-receiving body 2 is continuously height-adjustable in the vertical direction A or B and in the respective desired stroke position persistent and can be blocked or locked via the motor drive. For this purpose, the load-receiving body 2 and the undercarriage 3 in the illustrated embodiment are coupled in a pivotable manner with handlebar elements 4, 5 and 6, 7 arranged in pairs in the end regions. At their upper end in the drawing in the drawing have this the link elements 4, 5 on the one hand and 6, 7 on the other hand coaxially arranged pivot axes 8, 9 and 10, 11, which have a profile construction with down in the direction of the base 3 excellent bearing approaches and arranged therein holes are connected.

At its opposite end portion, the link elements 4, 5 on the one hand and 6, 7 on the other hand also on each with their longitudinal axes parallel to the Pivot axes 8, 9 and 10, 11 coaxial pivot axes 12, 13 and 14, 15 ( Fig. 3 ), each associated with a roller 16, 17 and 18, 19. The rollers 16-19 are each guided in pairs on the arranged in the end regions of the undercarriage 3 slide guides 20, 21 and 22, 23 smoothly. In the illustrated embodiment, the slide guides consist essentially of U-profiles, which are directed with their U-legs against each other, so with their U-legs to the longitudinal center axis 24 of the lifting table 1 and thus also the lower frame 3 have.

The link elements 4, 5 and 6, 7 have in their approximately central length ranges, at the same level in each case further, in pairs, coaxially arranged pivot axes 25, 26 and 27, 28, with which in each case a support lever 29, 30 and 31, 32, namely at the mutually facing inner sides of the link elements 4, 5 and 6, 7, is pivotally mounted.

At their respective opposite end portion, these support levers 29, 30 and 31, 32 are connected to a respective pivot shaft 33 and 34 of an associated transmission 35 and 36, respectively. The two gear 35, 36 are arranged symmetrically to the transverse center axis 37 on the base frame 3 or within its existing profile elements frame.

The gear 35, 36 are driven by a respective propeller shaft 38, 39, which in turn from a in the illustrated embodiment arranged on the transverse center axis 37, for example, as a reversible electric motor, in particular asynchronous motor or synchronous motor, formed drive motor 40, are driven. The power supply and the associated facilities to the drive motor 40 (electrical line, control cabinet) are not shown.

Symmetrically to the transverse center axis 37, a prestressed compression spring element 41 or 42 is arranged in the illustrated embodiment. Each compression spring element 41, 42 are by the load-receiving body 2 on the one hand and the undercarriage 3 on the other hand, each paired, coaxial with each other, peg-shaped or sleeve-like guide elements 43, 44 and 45, 46 mounted and guided, in the illustrated embodiment with a certain length positively engage in the compression spring elements 41 and 42. The compression spring elements 41 and 42 take up a considerable part of the load-receiving body 2 and the load, which can not be seen in the drawing, for example a body of a passenger car or a part thereof. The spring force of the compression spring elements 41, 42 is designed so that it significantly relieves the drive motor 40 at the beginning of the lifting movement. Thus, the drive motor can be designed much smaller, which means that considerable electrical energy can be saved by, for example, 40 to 50%, depending on the application.

In the illustrated embodiment, the stroke of the load receiving body 2 800 mm, the lifting speed to reach the full lift height, 2.6 seconds, the lifting weight 1,500 kg, while the lowest point ( Fig. 2 ) Is 600 mm.

The features described in the claims and in the description and apparent from the drawing features, both individually and in any combination for the realization of the invention may be essential.

reference numeral

1

Lift table

2

Load-bearing body

3

undercarriage

4

link element

5

"

6

"

7

"

8th

swivel axis

9

"

10

"

11

"

12

swivel axis

13

"

14

"

15

"

16

role

17

"

18

"

19

"

20

link guide

21

"

22

"

23

"

24

Longitudinal center axis of the lifting table 1

25

swivel axis

26

"

27

"

28

"

29

support lever

30

"

31

"

32

"

33

pivot shaft

34

"

35

transmission

36

"

37

Transverse center axis

38

propeller shaft

39

"

40

drive motor

41

Compression spring element

42

"

43

guide element

44

"

45

"

46

"

A

Lifting direction, vertical

B

"'"

Claims (23)

Motorized vertically adjustable lifting table (1), for example, for use in the bodywork of the automotive industry, with the ground floor associated frame-like base (3) and a relatively liftable load-receiving body (2) by pivoting link elements (4, 5 and 6, 7) relative to the underframe (3) in the vertical direction (A - B) liftable and in the respective height adjustment also immovably stoppable and, for example, motor lockable, in particular two or more spaced, against the load receiving body (2) supporting Compression spring elements (41, 42) which receive a significant portion of the weight transferred from the load-receiving body and to the link elements (4, 5 and 6, 7). Lifting table according to claim 1, characterized in that the compression spring elements (41, 42) on the one hand - also indirectly - against the underside of the load receiving body (2) and on the other hand - also optionally also indirectly - against the undercarriage (3) supported under spring bias. Lifting table according to claim 1 or 2, characterized in that the compression spring elements (41, 42) in the space between the link elements (4, 5 and 6, 7) are arranged. Lifting table according to one of claims 1 to 3, characterized in that the compression spring elements (41, 42) in the space at the end regions of the lifting table (1) between the load receiving body (2) and the lower frame (3) are arranged. Lifting table according to one of claims 1 to 4, characterized in that the compression spring elements (41, 42) are arranged in the bounded by mutually parallel boundary planes, which include the load-receiving body (2) and the base frame (3). Lifting table according to one of claims 1 to 5, characterized in that the compression spring elements (41, 42) are arranged asymmetrically with respect to the transverse center axis (37) of the underframe (3). Lifting table according to one of claims 1 to 6, characterized in that the compression spring elements (41, 42) asymmetrically with respect to the transverse center axis (37) of the undercarriage (3) and arranged asymmetrically with respect to the longitudinal center axis (24) of the lifting table (1) are. Lifting table according to one of claims 1 to 5, characterized in that the compression spring elements (41, 42) are arranged symmetrically with respect to the transverse center axis (37) of the underframe (3). Lifting table according to one of claims 1 to 5, characterized in that the compression spring elements (41, 42) on the longitudinal center axis (24) of the undercarriage (3) or in pairs symmetrically to this and symmetrically to the transverse center axis (37) of the undercarriage (3) arranged are. Lifting table according to claim 1 or one of claims 2 to 9, characterized in that each compression spring element (41, 42) by the load receiving body (2) on the one hand and the lower frame (3) on the other hand associated, in pairs, coaxial with each other, peg-shaped guide elements (43 , 44 or 45, 46), in particular sleeves, is mounted and guided, wherein the guide elements (43, 44 or 45, 46) engage with a certain length section in the respective compression spring element (41, 42), preferably with positive engagement. Lifting table according to claim 1 or one of claims 2 to 9, characterized in that each compression spring element (41, 42) by the load receiving body (2) on the one hand and the lower frame (3) on the other hand associated, in pairs, coaxial with each other, peg-shaped or sleeve-like guide elements (43, 44 or 45, 46), are stored and guided, wherein the guide elements (43, 44 and 45, 46) engage around the respective compression spring element (41, 42) with a certain length section, preferably in a form-fitting manner. Lifting table according to claim 1 or one of claims 2 to 11, characterized in that the compression spring elements (41, 42) counteract more than 10% of the total weight of the load receiving body (2) and, for example, its load, in particular 26% to 100%. Lifting table according to claim 1 or one of claims 2 to 12, characterized in that the compression spring elements (41, 42) are designed as helical compression springs. Lifting table according to claim 1 or one of claims 2 to 12, characterized in that the compression spring elements (41, 42) are designed as leaf spring elements. Lifting table according to claim 1 or one of claims 2 to 14, characterized in that the compression spring elements (41, 42) consist of spring steel. Lifting table according to claim 1 or one of claims 2 to 15, characterized in that by means of a z. B. controllable and reversible electric drive motor (40) via a respective propeller shaft (38, 39) more, z. B. a pair of arranged in the respective end region of the underframe link elements (4, 5 and 6, 7) - optionally indirectly - are driven to pivot. Lifting table according to claim 1 or one of claims 2 to 16, characterized in that on each longitudinal side in the respective end region of the lifting table (1) each two horizontal axes with the load receiving body (2) pivotally coupled link elements (4, 5 and 6, 7 ) are arranged, which at its opposite, the lower frame (3) associated end portions via slide guides (20, 21 and 22, 23) in the longitudinal axis of the undercarriage (3) are guided in a straight line, and that in the middle length region of each link element (4, 5 or 6, 7) via a horizontal pivot axis (25, 26 and 27, 28) depending on a support lever (29, 30 or 31, 32) is pivotally mounted, which at its opposite end portion via a likewise horizontal pivot axis with a pivot shaft (33, 34) of a transmission (35, 36) is connected, which is driven via the associated propeller shaft (38, 39). Lifting table according to claim 17, characterized in that the slotted guides (20, 21 or 22, 23) U-rails, whose U-legs are respectively directed to the inside of the underframe (3) and in which roller guides for the respective link element (4 , 5 and 6, 7) are guided rectilinearly and stored. Lifting table according to Claim 1 or one of Claims 2 to 18, characterized in that the drive motor (40) designed as a reversible electric motor, in particular an asynchronous motor or synchronous motor, is preferably in the middle length range, preferably approximately on the transverse center axis (37) of the undercarriage ( 3), z. B. central, is arranged. Lifting table according to claim 1 or one of claims 2 to 19, characterized in that the compression spring elements (41, 42) in the position in which the load-receiving body (2) and the lower frame (3) have the minimum distance from each other, about 100% of Weight of the load receiving body (2) and the load arranged thereon and decreases with increasing lifting movement to a much smaller amount, for example to about 10 to 30%, preferably to about 26% decreases. Lifting table according to claim 1 or one of claims 2 to 20, characterized in that at a total weight of load-carrying body (2) with a possible load of the load receiving body (2) of about 1,500 kg of the load receiving body (2) has a stroke of 0 to 600 mm in 2 seconds and a stroke of 0 to 800 mm in 2.6 seconds. Lifting table according to Claim 1 or one of Claims 2 to 21, characterized in that the drive motor outside the transverse center axis is associated with the underframe (3). Lifting table according to claim 1 or one of claims 2 to 18 or 20 to 22, characterized in that the drive motor is arranged with its longitudinal axis parallel or approximately parallel to the longitudinal center axis of the undercarriage (3).

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