Patent Abstract:
The invention relates to a weight compensation device for a drive of a lifting door, for the position-dependent compensation of the weight force of a door leaf of the lifting door, with a force transmission unit which can be coupled to the drive in order to carry out an opening movement which raises the door leaf and a closing movement which lowers the door leaf, wherein at least one compression spring is provided which is arranged in such a way that it supports the opening movement. The invention also relates to a lifting door, in particular an industrial lifting door, which has a door leaf, with a drive, such as a motor, and with a weight compensation device according to the invention.

Full Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is divisional application of and claims priority to U.S. patent application Ser. No. 14/361,394, filed on May 29, 2014, which is a national phase application of PCT Application No. PCT/EP2012/004697, filed Nov. 12, 2012, which claims priority to German Patent Application No. 10 2011 119 895.8 filed Nov. 29, 2011, all of these are incorporated by reference. 
     
    
     BACKGROUND AND SUMMARY 
       [0002]    The invention relates to a weight compensation device for a drive of a lifting door for the position-dependent compensation of the weight force of a door leaf of the lifting door, with a force transmission unit which can be coupled to the drive in order to carry out an opening movement which raises the door leaf and a closing movement which lowers the door leaf. 
         [0003]    A generic weight compensation device is known from GB 570,469. 
         [0004]    From prior art, lifting doors with integrated weight compensation devices are moreover known. For example, DE 40 15 214 A1 discloses a lifting door with a slatted armor with bending slats. The lifting door disclosed therein comprises two guide tracks disposed at the two opposite sides of the door aperture, and a slatted armor with slats placed on hinge straps at such a distance to each other that the hinge pins engage within a space between the adjoining slats. It is furthermore disclosed that this lifting door is configured as an industrial lifting door in the sense of a high-speed lifting door. Such lifting doors are configured as rolling doors which close or open walk-through or drive-through door apertures. 
         [0005]    It is known from DE 40 15 214 A1 that tension springs are employed for compensating the weight of the individual slats forming the door leaf. However, a disadvantage of tension springs consists in that they only have a service life of about 200,000 lifts. 
         [0006]    Torsion springs employed as an alternative have an even shorter service life of about 30,000 to 40,000 lifts. 
         [0007]    The often employed tension springs even have yet another disadvantage, i. e. they require a lot of installation space for heavy doors which must be available in particular at the sides of the door aperture. If a frame of the door is not wide enough to receive adjoining tension springs which provide the required supporting spring force, it is also possible to dispose them one behind the other, but both types affect efficient space utilization in the region of a lifting door. 
         [0008]    From prior art, alternative weight compensation devices which are employed, for example, in sectional doors, are also known. For example, DE 102 32 577 A1 discloses a weight compensation device for a sectional door with a rotatably mounted shaft, a rope drum at least at one end of the shaft on which a traction rope connected to the door leaf of the sectional door is connected, and at least one torsion spring configured as a coil spring. The coil spring is retained at one spring end at a stationary receiving part and at the other spring end at a receiving body fixed to the shaft and acts as torsion spring having a particularly short service life. 
         [0009]    Even the employment of hydraulic accumulators in industrial lifting doors does not represent an optimal embodiment because constructions employing such hydraulic accumulators are expensive and complex. 
         [0010]    It is therefore the object of the present invention to avoid the disadvantages of prior art and to provide an inexpensive, long-life weight compensation device which may be employed in doors where foil-like door leaves or several hinged, preferably rigid segments are lifted, such as spiral doors or doors that employ the drum principle. 
         [0011]    This object is achieved according to the invention by a weight compensation device having the features disclosed herein. Such compression springs may bear higher loads over years as compared to tension and especially torsion springs, without any failure occurring already after a relatively short time of use or maintenance works having to be performed at an early stage. In tests performed at certain compression springs, no essential spring deformations showed after one million lifts. The compression spring is arranged in a hollow-cylindrical guide element, the hollow-cylindrical guide element being attached to a mount so as to rotate or, alternatively, in a torque-proof manner, for supporting a rotary motion of the force transmission unit. This permits efficient spring force utilization with a compact design. 
         [0012]    A solution according to the invention is therefore not only inexpensive and long living, but also permits the advantage of a particularly simple and efficient construction. 
         [0013]    Advantageous embodiments are claimed in the subclaims and will be illustrated more in detail below. 
         [0014]    For example, it is advantageous for the compression spring to be coupled to a motion conversion device which employs the force acting in the longitudinal direction to the compression spring for supporting a rotary motion of the force transmission unit that raises or lowers the door leaf. The motion conversion device therefore utilizes the force that can be stored in a compression spring to transfer a supporting torque to the force transmission unit. 
         [0015]    It is furthermore advantageous for the compression spring to be arranged essentially horizontally, preferably transversely to the lifting or lowering direction of the door leaf. Thereby, the installation space may be well utilized. 
         [0016]    The weight compensation device may be particularly compactly realized when the door leaf surrounds a hollow space in its lifted, wound-up state where the compression spring and/or the motion conversion device are arranged. 
         [0017]    To be able to realize spiral doors and drum doors in a particularly easy way, it is advantageous for the guide element to embody a torque-proof hollow cylinder, or for the guide element to embody the drive shaft configured as hollow shaft. 
         [0018]    The force of the compression spring may be particularly efficiently used as supporting torque for compensating the weight of the door leaf if the compression spring supports itself at a base part fixed with respect to the guide element and an adjusting element translationally movable relative to the guide element with force transmission. 
         [0019]    An advantageous embodiment is characterized in that the drive shaft is in active relation with the adjusting element which is movable in a longitudinal direction of the drive shaft by the compression spring. 
         [0020]    A transmission-like embodiment may be achieved if the adjusting element is coupled to the drive shaft so as to transmit torques, preferably in such a way that a movement of the adjusting element along the longitudinal direction enforces torque transmission from the adjusting element to the drive shaft. 
         [0021]    In order to avoid any rotation of the adjusting element, for example when the drive shaft is rotating, it is advantageous for the adjusting element to be guided within the hollow shaft so as to be movable in the longitudinal direction, preferably in a groove on the inner side of the hollow shaft which preferably extends essentially in the longitudinal direction. However, it is also possible for the groove to be present at the adjusting element and corresponding diametrically opposed projections to be present on the inner side of the hollow shaft. 
         [0022]    If the adjusting element is configured as a spindle nut, one may use a tried and tested conversion element. By this, high forces may be transmitted and components be used that are loadable over a long time. 
         [0023]    It is particularly suitable for the spindle nut to be coupled to the drive shaft by threaded engagement. The spring force of the compression spring may be then particularly easily supportively impressed on the drive shaft. 
         [0024]    A further advantageous embodiment is characterized in that at least one flexible clutch is embodied in the drive shaft which splits up the latter. Such a flexible clutch, in particular of a claw clutch type, is advantageous for compensating a mechanical overdetermination between lateral bearings which are employed for mounting the drive shaft. It is possible to only use plain bearings on the one side of the claw clutch, whereas on the other side of the claw clutch, a thrust bearing and a plain bearing are combined. It is also possible to use several flexible clutches, such as claw clutches, axially one behind the other and to arrange the corresponding bearings outside these flexible clutches. 
         [0025]    The invention also relates to a lifting door, in particular an industrial lifting door, which comprises a door leaf, with a drive, such as a motor, and an inventive weight compensation device as illustrated above. Such a motor may be, for example, an electric motor or a hydraulic or pneumatic motor. Even internal combustion engines are possible power units. 
         [0026]    It is then furthermore advantageous for a control window to be provided in the hollow shaft which permits a view to the spindle nut. In this manner, the adjustment of the individual elements with respect to each other becomes controllable. 
         [0027]    It is advantageous for the control window to extend along the longitudinal direction and to be preferably oriented horizontally, so that a readjustment or an initial adjustment of the individual elements may be particularly easily controlled. Such a horizontal orientation offers itself especially due to the fact that the hollow shaft, i. e. the drive shaft, is normally arranged such that it extends above the door aperture in the horizontal direction. 
         [0028]    If the spindle nut comprises an end plate for which an assembly position is marked in the control window, even untrained personnel may easily perform adjustment and assembly. 
         [0029]    It is furthermore advantageous if during the assembly of the lifting door, the coupling between the motor and the spindle nut may be cancelled to bring the spindle nut into a desired assembly position preferably manually and/or using a crank, where coupling may be restored in this position. In this context, a method which uses the control window to bring the end plate, after a decoupling of the corresponding elements, back into the planned position and then restore the coupling is also advantageous. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0030]    The invention will be illustrated more in detail with reference to the drawing in which different embodiments are represented in different views. In the drawings: 
           [0031]      FIG. 1  shows a first weight compensation device according to the invention for a spiral door, 
           [0032]      FIG. 2  shows a slightly modified weight compensation device of  FIG. 1  in a side view, 
           [0033]      FIG. 3  shows a weight compensation device of  FIG. 1  in a longitudinal sectional view as in  FIG. 1 , however in a position in which, different from  FIG. 1 , the door aperture is closed, 
           [0034]      FIG. 4  shows a front view of a spiral lifting door with the weight compensation device of  FIGS. 1 to 3  in a partial longitudinal sectional representation where the weight compensation device has assumed a position which is present when the door leaf is raised, while in  FIG. 4 , the door leaf is shown in a lowered position, 
           [0035]      FIG. 5  shows a view of the lifting door of  FIG. 4  from above, 
           [0036]      FIG. 6  shows a side view of the spiral lifting door of  FIGS. 4 and 5  with a plug-in drive, 
           [0037]      FIG. 7  shows the variant of a lifting door of  FIGS. 4, 5 and 6 , however with a straight bevel gear drive and a sprocket belt, 
           [0038]      FIG. 8  shows an enlarged sectional representation of the straight bevel gear drive of  FIG. 7 , 
           [0039]      FIG. 9  shows a weight compensation device for a lifting door which realizes a drum winding in a partial longitudinal sectional representation, the weight compensation device being shown in a position where the door aperture is unclosed, i. e. the door is held open, 
           [0040]      FIG. 10  shows a view from the side onto the slightly modified weight compensation device of  FIG. 9 , 
           [0041]      FIG. 11  shows a partial longitudinal sectional view of the weight compensation device of  FIG. 9 , but in a closed position, i. e. in a position where the door aperture is closed by the door, 
           [0042]      FIG. 12  shows a view of a lifting door in which the weight compensation device of  FIG. 9  is employed which is shown in a position assumed when the door leaf is in a lifted, opened position, the door leaf itself, however, being shown in a closed position in  FIG. 12 , 
           [0043]      FIG. 13  shows a view onto the door of  FIG. 12  from above, 
           [0044]      FIG. 14  shows a side view of the door of  FIGS. 12 and 13  with a plug-in drive, 
           [0045]      FIG. 15  shows a side view of the door of  FIGS. 12 to 14 , but in the variant of a cylindrical drive with a sprocket belt instead of a plug-in drive, 
           [0046]      FIG. 16  shows an enlarged schematic diagram of the cylindrical drive with a sprocket belt of  FIG. 15  in a front view, 
           [0047]      FIG. 17  shows a schematic diagram of the different spring positions of the compression spring, and 
           [0048]      FIG. 18  shows a torque diagram for the compression spring with a fixed motor torque. 
       
    
    
     DETAILED DESCRIPTION 
       [0049]    The figures are only schematic drawings and only serve the understanding of the invention. Identical elements are provided with identical reference numerals. 
         [0050]      FIG. 1  shows a first embodiment of a weight compensation device  1 . The weight compensation device  1  is provided for being employed at a drive  2 . The drive  2  comprises a motor  3 , such as an electric motor. The weight compensation device is provided for compensating the weight of a door leaf  4  depending on the position of the door leaf shown, for example, in  FIG. 4 , the door leaf being the so-called curtain, assembled from several segments  5  as required. 
         [0051]    The weight compensation device comprises a force transmission unit  6 . The force transmission unit is designed for activating a raising motion, i.e. an opening motion, and a lowering motion, i. e. a closing motion, of the door leaf  4 . The force transmission unit  6  is thus directly or indirectly connected to the door leaf  4 , i. e. at least one segment  5  of the door leaf  4 . 
         [0052]    In the variant for embodying a spiral door represented in  FIG. 1 , the individual segments  5  are guided at their sides within a spiral or a spiral guide  40  without the segments  5  coming into contact with each other during the winding process. A continuous traction member  7 , such as a belt or a chain, functions as drive member for driving the force transmission unit  6 . 
         [0053]    The force transmission unit  6  is embodied as drive shaft  8 . The drive shaft Bis mounted via four bearings  9 , in particular bearings  9  configured as rolling bearings.  FIG. 1  shows a position in which the door is opened. On the right side of the weight compensation device  1 , a thrust bearing is provided on the inner side of a right-hand continuous traction member  7 , whereas a plain bearing is provided on the outer side. On either side of the continuous traction member  7  located on the left side of the weight compensation device  1 , several bearings  9  configured as plain bearings are provided. 
         [0054]    By means of the drive  2  of the force transmission units  6 , i. e. the drive shaft  8 , the door leaf  4  is held so that it may be raised and lowered. 
         [0055]    A spindle nut  10  is provided on the drive shaft  8  so as to grip around the latter, the spindle nut comprising an end plate  11 . The end plate  11  is located in a stationary hollow shaft  12 . At least one projection  13  of the end plate  11  is positively locked with a groove  14  on the inner side  15  of the hollow shaft  12 . The groove  14  is a longitudinal groove, i. e. a groove extending in parallel to the longitudinal axis  16  of the drive shaft  8 . 
         [0056]    A preferably metallic compression spring  17  is provided concentrically to the longitudinal axis  16 . The compression spring  17  is configured as flat spiral spring extending along the longitudinal axis of the hollow shaft  12 . The compression spring  17  is a component which is in a solid aggregation state under normal pressure and temperature conditions that normally prevail in the surrounding area. It is a metallic component which acts in an elastically restituting manner. Being relieved, it returns to its original shape. Here, it is embodied as a wound spring. 
         [0057]    The compression spring  17  is prestressed by the value Δ v  between the end plate  11  and a base part  18 . The base part  18  is in this embodiment connected to the hollow shaft  12  in a torque-proof and axially fixed manner. For the compression of the compression spring  17 , it is relevant that it is disposed between the base part  18  and the adjusting element  37 , such that it may be translationally compressed. 
         [0058]    It is also possible for the base part  18  to be replaced by an embodiment similar to an adjusting element such that this component similar to an adjusting element is present on the same spindle as the spindle nut  10 . The two parts are then arranged on threads running in opposite directions. 
         [0059]    Projecting from the end plate  11  in the direction of the base part  18 , a bushing  19  is embodied which may be integrally formed with the end plate  11  or may be connected to it with a form-fit, a frictional connection and/or by a material bond. On the inner side of the bushing  19 , a thread is formed which is in threaded engagement with a threaded section  20  of the drive shaft  8 . 
         [0060]    The drive shaft  8  is split into three parts, where in the transitional region between the individual parts of the drive shaft  8 , one flexible clutch  21 , in particular of a flexible claw clutch type, is provided each. 
         [0061]    In operation of the spiral door, the hollow shaft  12  is standing still, whereas the drive shaft  8  is rotatable. Depending on the compression state of the spring  17 , more or less torque is applied to the drive shaft  8  by means of the spindle nut  10  by the longitudinal displacement of the end plate  11  via the threaded engagement of the bushing  19 . 
         [0062]    In  FIG. 2 , two diametrically opposed projections  13  of the spindle nut  10  can be seen which are engaged in two longitudinal grooves, i. e. grooves  14  which extend in the longitudinal direction, i. e. in parallel to the longitudinal axis  16 . It is also possible for the groove  14  to be provided in the hollow shaft  12  of an external tube-type or the spindle nut  10 . 
         [0063]      FIG. 3  shows a detail of the weight compensation device  1  in the position where the door is closed. The interior of the hollow shaft  12  is represented in a dot-dash line, where now the end plate  11  is spaced apart from a left end of the hollow shaft or an extension of the hollow shaft by a distance Δ v +s. Δ v  designates the path caused by the spring tension, and s designates the spring trajectory caused by the adjustment. 
         [0064]    A control window  22 , i. e. an opening in the wall of the hollow shaft  12 , is formed which permits a view to the end plate  11 . In the central region of the control window  22 , a widening  23  is present which represents a mark for an optimal assembly position. 
         [0065]      FIGS. 4 to 7  show the complete lifting door in three views, where in  FIG. 6 , a drive  2  configured as plug-in drive  24  is employed, and in the variant as it is shown in  FIG. 7 , instead of the plug-in drive  24 , a straight bevel gear drive  25  with a sprocket belt  26  is employed. 
         [0066]    A frame width is only determined by a door leaf guide  39  and possibly also by the continuous traction member  7 . In the variant shown in  FIGS. 1 to 8 , the frame width is determined by both components, whereas in the embodiment of  FIGS. 9 and 16 , the width is exclusively determined by the door leaf guide  39 , because no continuous traction member  7  is present, and the drive is realized via the hollow shaft  12 . 
         [0067]    In  FIG. 8 , a further cross-section of  FIG. 7  is shown by which a so-called “longitudinal arrangement” may be realized. The motor may be arranged to be aligned with the frame, permitting a particularly efficient saving in space. In particular also by the arrangement of the compression spring  14  remote from the frame, the frames may be kept relatively narrow. These arrangements of the motor and the compression spring may be generally realized in all shown embodiments of the invention. 
         [0068]    Different to prior art, the spring configured as compression spring is not arranged in the vertical direction but in the horizontal direction within the hollow shaft  12  so as to surround the drive shaft  8 . 
         [0069]    The compression spring  17  is located in a hollow space  33 . The hollow space  33  is defined by the wound-up door leaf  4 . The door leaf  4  is guided in the spiral guide  40  and surrounds the hollow space  33  in its wound-up state. 
         [0070]    A motion conversion device  32  is coupled to the compression spring  17  and comprises at least the base part  18 , the pressure element  34  which is configured as hollow cylinder  36  and has in particular assumed the shape of the hollow shaft  12  and comprises the groove  14  extending in the longitudinal direction on its inner side, and an adjusting element  37  which is configured as spindle nut  10  with a bushing  19  and an end plate  11 . 
         [0071]    The motion conversion device  32  converts the rotary drive energy into a translational kinetic energy. 
         [0072]    The compression spring  17  is arranged horizontally between two vertical frames  50  of a mount  35 . 
         [0073]      FIG. 9  shows a second embodiment of a weight compensation device  1  which is also represented in an opened door position. The drive shaft  8  is connected to the hollow shaft  12  in a torque-proof manner, so that the hollow shaft  12  may be rotated in the sense of a drum, and when the door is being opened, the individual segments  5  of the door leaf  4  are wound onto the hollow shaft  12  like on a drum. The door leaf  4  may also have a foil-like character and then be just as easily wound up. The spindle nut  10  also comprises an end plate  11  and a bushing  19 , as in the first embodiment. The bushing  19  has a threaded engagement section which is provided with reference numeral  27 . This threaded engagement section  27  engages a threaded section  20  of a stationary shaft  28 . The shaft  28  is firmly connected to the base part  18 . 
         [0074]    The end plate  11  comprises projections  13  which are guided in a groove  14  formed on the inner side  15  of the hollow shaft  12  in the longitudinal direction. One projection  13  each is guided in one groove  14  each. The base part  18  also comprises such projections  13  which are also guided in one groove  14  each. However, it is also possible for the compression spring  17  configured as base part  18  to be connected to the hollow shaft  12  in a torque-proof and/or translationally fixed manner by a form-fit, a frictional connection, and/or a material bond. 
         [0075]    In the illustrated second embodiment, the drive shaft  8  is connected to the hollow shaft  12  in a torque-proof manner. In this embodiment, as can be seen in  FIG. 10 , one does not rely on only two opposed projections  13  at the end plate  11 , but four projections  13  which have the same angular distance with respect to each other. 
         [0076]    As can also be seen in  FIG. 10 , the projections or grooves may be either located at the one component or at the other component as long as a longitudinal guidance is ensured. It is principally also conceivable to interchange the positions of the longitudinal guiding elements and screw elements. 
         [0077]    In all embodiments, the compression spring may optionally support itself radially in the hollow-cylindrical guide element  34 , preventing a buckling of the spring. 
         [0078]    The base part of  FIG. 9  also comprises an extension section  38  which permits to shorten the stationary shaft  28  with the threaded section  20 . 
         [0079]    As was already stated with respect to the embodiment according to  FIGS. 1 to 8 , the second embodiment of  FIGS. 9 to 16 , too, comprises a control window  22 , where here, however, a plate-like section of the base part  18  can be seen. The base part  18  may be interchanged with the spindle nut  10 , if desired. 
         [0080]    In  FIGS. 13 and 15 , the door leaf  4  is, for illustration reasons, shown with a control window  41  and a termination shield (not shown) in a position closing the passage, although the compression spring  17  is in a relieved position. 
         [0081]    Views corresponding to the views shown in  FIGS. 4 to 8  with respect to the second embodiment of the weight compensation device  1  are shown in  FIGS. 12 to 16 . 
         [0082]    In  FIG. 17 , three positions of the compression spring  17  are shown, which are a non-stressed compression spring  17  leftmost, a prestressed spring in the middle, and a completely stressed compression spring  17  rightmost. In operation, the compression spring  17  is in its maximal positions in a state in accordance with the central and right positions. 
         [0083]      FIG. 18  shows a spring tension relative to a present motor torque M, where the continuous first line  29  represents the torque T t  caused by the weight of the door leaf  4  in response to its position, and the dashed second line  30  represents the torque T f  caused by the spring. The torque moment is designated with M and is the distance between lines  29  and  30 . From the maximum opening position, a compensation point  31  is achieved by the intersection of both lines  29  and  30 , so that a deceleration of the door leaf is achieved just before the maximum opening position. 
         [0084]    In the embodiment visualized in  FIGS. 9 to 16 , too, the compression spring  17  is located in a hollow space within the wound-up door leaf  4 . 
         [0085]    Embodiments which are designed corresponding to the following computations proved to be particularly advantageous: 
         [0086]    1. Door Leaf-Related Torque: 
         [0087]    Door leaf weight: G t =115 kg 
         [0088]    Crown gear diameter: d o =75 mm 
         [0089]    g: Gravitational acceleration 9.81 m/s 2   
         [0000]    
       
         
           
             
               
                 T 
                 t 
               
               = 
               
                 
                   
                     F 
                     t 
                   
                   · 
                   a 
                 
                 = 
                 
                   
                     
                       G 
                       t 
                     
                     · 
                     g 
                     · 
                     
                       
                         d 
                         o 
                       
                       2 
                     
                   
                   = 
                   
                     115 
                     · 
                     9 
                   
                 
               
             
             , 
             
               
                 81 
                 · 
                 
                   75 
                   2 
                 
               
               = 
               42 
             
             , 
             
               3 
                
               
                   
               
                
               Nm 
             
           
         
       
     
         [0090]    2. Spring-Related Torque: 
         [0091]    Spring force F f =9000 N 
         [0092]    Spindle diameter 40 mm, pitch P h =40 mm 
         [0093]    Efficiency with linear rotation η 2 =0.98 
         [0000]    
       
         
           
             
               
                 T 
                 f 
               
               = 
               
                 
                   
                     
                       F 
                       f 
                     
                     · 
                     Ph 
                     · 
                     
                       η 
                       2 
                     
                   
                   
                     2 
                      
                     π 
                   
                 
                 = 
                 
                   
                     
                       
                         9000 
                         · 
                         40 
                         · 
                         0 
                       
                       , 
                       98 
                     
                     
                       2 
                        
                       π 
                     
                   
                   = 
                   56 
                 
               
             
             , 
             
               2 
                
               
                   
               
                
               Nm 
             
           
         
       
     
         [0094]    3. Required Motor/Driving Torque 
         [0000]        T   m   =T   f   −t   l =56.2−42.3=13.9 Nm

Technology Classification (CPC): 4