Abstract
A load-compensating device for a lifting application with an object to be lifted or lowered includes a movable platform, wherein the platform carries the object and, for purposes of load compensation, the platform is supported by at least one spring element that acts on a spreading unit which, in order to achieve spreading, transfers a spring force of the spring element into a scissors arrangement, where, by virtue of the scissors arrangement, the spring force results in a lifting force that produces a lifting action on the platform, and where a substantially constant lifting force is provided over a substantial lifting distance of the platform by the lifting geometry formed via the spreading unit and the scissors arrangement.
Claims
1.-5. (canceled)
6. A load-compensating device for a lifting application with an object to be lifted or lowered, comprising: a movable platform which carries the object, the platform being supported by at least one spring element to compensate for loads; wherein the spring element acts on a spreading unit which, in order to achieve spreading, transfers a spring force of the spring element into a scissors arrangement; wherein, by virtue of the scissors arrangement, the spring force acts as a resultant lifting force, exerting a lifting action on the platform; wherein a substantially constant lifting force is provided over a substantial lifting distance of the platform by lifting geometry formed via the spreading unit and the scissors arrangement; and wherein the spring element is configured as at least two tension springs acting in parallel and is prestressed with a spring prestress at a level such that the spring element is formed as a block in an upper lifting position.
7. The load-compensating device as claimed in claim 6, wherein the spreading unit has thrust rods which are each articulated between the spring element and a scissor arm of the scissors arrangement.
8. The load-compensating device as claimed in claim 6, wherein the spreading unit acts on a cam geometry; and wherein a cam geometry predetermines a profile of a lever action of the spreading unit on the scissors arrangement.
9. The load-compensating device as claimed in claim 7, wherein the spreading unit acts on a cam geometry; and wherein a cam geometry predetermines a profile of a lever action of the spreading unit on the scissors arrangement.
10. The load-compensating device as claimed in claim 8, wherein the cam geometry is formed by at least one curved surface of a scissor arm of the scissors arrangement; and wherein the spring force acts on the curved surface via the spreading unit via a slider or a roller structure.
11. The load-compensating device as claimed in claim 6, wherein the spreading unit has a spreading wedge geometry on at least one side.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0019] Exemplary embodiments of the load-compensating device according to the invention and advantageous embodiments are described below with reference to the drawings, in which:
[0020] FIG. 1 shows a schematic illustration of two embodiments A1, A2 of the mechanism kinematics of the load-compensating device with thrust rods as a spreading device in accordance with the invention,
[0021] FIGS. 2-5 show a schematic illustration of further embodiments B, C, D, E of the mechanism kinematics of the load-compensating device with alternative spreading devices in accordance with the invention,
[0022] FIG. 6 shows a technical implementation of embodiment A1 with a vertical guidance function in a lowered (lower) position and an extended (upper) position,
[0023] FIG. 7 shows a technical implementation of embodiment D with a vertical guidance function in a lowered (lower) position and an extended (upper) position,
[0024] FIG. 8 shows a technical implementation of embodiment D without a vertical guidance function in a lowered (lower) position and an extended (upper) position,
[0025] FIG. 9 shows a technical implementation of an integration of embodiment D into an existing lifting and lowering conveying device,
[0026] FIG. 10 shows a technical implementation of embodiment D as a lift table with an electric-cylinder/double-motor drive in a lowered (lower) position and an extended (upper) position, and
[0027] FIG. 11 shows a technical implementation of embodiment A1 as a lift table with a push-chain/double-motor drive in a lowered (lower) position and an extended (upper) position.
DETAILED DESCRIPTION OF THE EXEMPLARY EMBODIMENTS
[0028] On the left, in schematic form, FIG. 1 shows two embodiments A1, A2 of the mechanism kinematics of the device in accordance with the invention with mechanism elements, and, on the right, it shows the respectively associated force/lifting profile. The figure illustrates two centrally connected scissor arms (3), which are pivotable relative to one another and to each of which two likewise pivotably mounted thrust rods (4) are attached, where the opposite end of the thrust rods is coaxially mounted. A spring energy accumulator (5), which is likewise coaxially mounted and that acts in tension, is attached thereto. For the sake of clarity, the movable platform via which the force associated with the weight of the object to be moved is introduced into the arrangement is not shown in the schematic illustrations in FIGS. 1-5.
[0029] The spreading apart of the scissor arms (3) is achieved via the thrust rods (4) via the tensile force emanating from the energy accumulator (spring assembly). Consequently, the compensating force (F) acts on the ends of the scissor arms.
[0030] If it is possible, based on the application, to dispense with a rectilinear vertical guidance function, the floating bearing guides (2) of embodiment A1 can be eliminated, resulting in turn in installation space and cost advantages. This embodiment is illustrated schematically in the lower half of FIG. 1 via embodiment A2.
[0031] It is likewise possible to attach a lifting cam geometry (7) (lifting cam or cam geometry for short) to the scissor arms (3) on the same side as the fixed or floating bearings instead of the thrust rods in order in this way to achieve spreading of the scissors (3) via a spreading shaft running along the lifting cam; such embodiments D and E are shown in FIGS. 4 and 5. NB: The reference sign (3) is used below both for the scissor mechanism (scissors for short) and for a single scissor arm.
[0032] FIGS. 2, 3 and 5 show embodiments B, C and E. These solutions respectively comprise the spreading wedge mechanism in different combinations and are suitable particularly for spring accumulators with shallow characteristics, which have commercially available tension springs or, advantageously, oval wire tension springs, for example. With the adaptation of the lifting cam geometry (embodiments D and E), it is furthermore possible to adjust the force/lifting profile in an optimum manner.
[0033] The selected ratios of the scissor-arm and thrust rod lengths in conjunction with the position of the pivoting axes and the spring characteristic and optionally the configuration of the lifting cams make it possible to influence the force/lifting profile of the device. From the schematically illustrated force/lifting profile in FIG. 1, it can be seen that it is possible to achieve a virtually constant lifting force. If the actual force profile is compared with an ideally acting constant force profile, then linearity deviations of less than 1% are technically achievable. A linearity deviation of 15% is regarded as an upper limit in respect of the cost-benefit ratio.
[0034] As already described with reference to embodiment A2, it is also possible to dispense with the floating bearing guide shown in embodiments B, C, D and E if a rectilinear vertical guidance function is not required based on the application or if the lifting platform already has a vertical guide. This is often the case when existing lifting devices are retrofitted with a load-compensating device.
[0035] Technical possibilities for implementation of the embodiment from FIG. 1 and embodiment D from FIG. 4 as well as examples of use thereof are indicated below; embodiments B, C and E show modifications in other combinations of spreading structure.
[0036] FIG. 6 shows a technical implementation of embodiment A1. This explains the interaction between the mechanism elements of the mechanism. The spring accumulator integrated into the lifting mechanism here consists of a spring assembly that is made up of two compression springs mounted one inside the other. These are incorporated mechanically between the thrust rods such that the spring accumulator unit acts like a tension spring. The use of massive compression springs makes it possible to achieve a particularly high power density.
[0037] FIG. 7 shows a first technical embodiment of D (FIG. 4) with a rectilinear vertical guidance function of the load-compensating device according to the invention. Here, 4 high-power oval-wire tension springs acting in parallel serve as the spring accumulator, which have a higher power density, higher spring prestresses and lower spring rates than round-wire tension springs. With the number of springs, it is possible to increase or reduce the compensation load; for this purpose, it is also possible to provide coupling structure (not illustrated) to be able to respond to different loads in operation. In the example shown, the lifting cam is part of the scissor-arm contour, where the spreading shaft is guided axially by means of a centrally installed shaft.
[0038] FIG. 8 shows a technical embodiment of D (FIG. 4) without a guidance function, with 4 oval-wire tension springs acting in parallel as an energy accumulator. In this embodiment, the guidance on the floating-bearing side has been dispensed with, thereby eliminating the rectilinear vertical guidance function. Here, guidance of the spreading shaft along the centrally installed lifting cam is advantageously accomplished via a profiled running roller. An increase in the compensation force is achieved via the pairwise addition of spring elements. It is thus also technically possible to operate the embodiment shown in FIG. 8 with, for example, just 2 or with 6 or 8 tension springs acting in parallel. With the high spring prestress incorporated into the oval-wire tension springs, it is possible to generate the desired compensation force without having to additionally prestress the springs. The tension springs are in the form of a block in the upper lifting position. As a result, there is no need here to take any additional measures to disconnect the force or energy of the energy accumulator in the case of maintenance.
[0039] FIG. 9 shows the integration of two load-compensating devices from FIG. 5 acting in parallel into an existing lifting and lowering conveying device. This lifting and lowering conveying device is used to convey a bodyshell in the series manufacture of motor vehicles. In industry, there is often a desire to increase the performance of existing plants. In this example, integration of embodiment D from FIG. 4 in part relieves the load on the lifting mechanism with drivetrain and in part increases the load bearing capacity of the device (in this case by 40%). This retrofitting is associated with relatively little effort, and expensive overall reconstruction of the lifting and lowering conveying device for higher loads is eliminated. As a result, this results in considerable economic advantages.
[0040] Another area of use for load-compensating devices are lifting applications that are used on driverless transport vehicles (DTV). Here, the aspect of energy saving and increasing power is particularly prominent because the provision or supply of energy is associated with a high outlay and, in most cases, the lifting power is the limiting factor in this regard.
[0041] In the case of the load-compensating device shown in FIG. 10 for a DTV, both a vertical guidance function and a driving function have been integrated, resulting in the use as a lift table.
[0042] The load-compensating device illustrated in FIG. 11 with a guidance and driving function can be used as a lift table for high loads up to 3 t on driverless transport vehicles. Here, the driving function is provided by two push-chain drives synchronized electrically with one another, and the vertical guidance and load-compensating function is provided by two centrally installed load-compensating devices from FIG. 6.
[0043] Thus, while there have been shown, described and pointed out fundamental novel features of the invention as applied to a preferred embodiment thereof, it will be understood that various omissions and substitutions and changes in the form and details of the devices illustrated, and in their operation, may be made by those skilled in the art without departing from the spirit of the invention. For example, it is expressly intended that all combinations of those elements that perform substantially the same function in substantially the same way to achieve the same results are within the scope of the invention. Moreover, it should be recognized that structures and/or elements shown and/or described in connection with any disclosed form or embodiment of the invention may be incorporated in any other disclosed or described or suggested form or embodiment as a general matter of design choice. It is the intention, therefore, to be limited only as indicated by the scope of the claims appended hereto.
