Abstract:
The invention concerns a spring system for use in vehicles for adjustment of the suspension characteristics, comprising at least one spring element to provide a spring force, an upper and a lower arrangement area to receive forces, a scissors-type frame arranged between the upper and the lower arrangement area for coupling the spring element with at least one force acting on one of the arrangement areas. According to the invention the spring element is coupled with a deflection means to influence the spring force and between the deflection means and a segment of the scissors-type frame an active connection can be created to transmit forces.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is a convention application of German Application Serial Number 10 2009 031 411.3, filed Jul. 2, 2009 and German Patent Application No. 10 2009 040 010.9, filed Sep. 3, 2009, which applications are hereby incorporated by this reference in their entirety. 
       BACKGROUND OF THE INVENTION 
       [0002]    The invention concerns a spring system for use in vehicles, in particular for vehicle seats and/or vehicle cabs, according to the preamble of claim  1 . 
         [0003]    Spring systems, in particular for vehicle seats, are known in many variants. For example, very often a pneumatic spring is arranged between two suspension parts, namely a lower part and an upper part on which the actual vehicle seat is mounted, and in addition a gas damper element is fitted in order to absorb the vibration movement which can be initiated both from above by the driver and from below by the chassis. Such spring systems require a complex control of the air spring and the damper and are therefore cost- and time-intensive to produce and maintain. 
         [0004]    Such spring systems also have the disadvantage that after a certain time they require repair, and where applicable the air springs and/or dampers must be replaced. Furthermore the spring systems known from the prior art are often very complex to adjust. 
         [0005]    Consequently the present invention in based on the object of preparing a spring system for use in vehicles which can not only be produced economically but also is less time intensive to maintain and is simple in construction. Furthermore the spring system is easier to handle than spring systems known from the prior art. 
         [0006]    This object is achieved according to the invention by the object of claim  1 . 
       SUMMARY OF THE INVENTION 
       [0007]    The main aspect of the invention is that in a spring system for use in vehicles for adjusting suspension characteristics at least one spring element is provided which supplies a spring force, wherein between an upper and a lower arrangement area, both of which serve to absorb forces, a scissors-type frame is provided to couple the spring element with at least one force acting on one of the application areas. According to the invention the spring element is coupled with a deflection means to influence the spring force, and between the deflection means and a segment of the scissors-type frame an active connection can be created to transmit forces. 
         [0008]    This solution is advantageous in relation to devices known from the prior art as it simple and cheap to produce and easy to operate. 
         [0009]    As a active connection can be created to transmit forces between the deflection means and at least one segment of the scissors-type frame, different directions for the spring force emitted by the spring element can be set depending on the momentary position of the segment of the scissors-type frame. Since a first end of the spring element and the deflection means are coupled together at a connection point and for example the deflection means is a lever arm which at its other end is attached to an axis on the segment, different deflection positions of the deflection means depending on the momentary height setting of the segment of the scissors-type frame can generate different alignments of the spring force direction, leading to a different suspension characteristic. As a result an optimum vibration change can be achieved irrespective of the weight of the driver using the driver&#39;s seat. 
         [0010]    The coupling between the spring element and the deflection means allows, in case of a deflection of the deflection means, a force application of the spring element and vice versa. Furthermore the connecting point is arranged at a defined distance from a rotary axis of the deflection means as already stated. This is advantageous as despite the same connection point, depending on the position of the deflection means, different moments or lever ratios can be generated. Since the effective lever depends on the direction of the spring force and hence on the momentary deflection of the deflection means. A line oriented perpendicular to the direction of the spring force passing through the rotary axis of the deflection means gives the effective lever arm and hence the effective torque. 
         [0011]    Preferably here the angle between the deflection means and the extent or course of the segment of the scissors-type frame is firmly set irrespective of the momentary deflection angle of the deflection means. This means that if the segment is in a flatter position i.e. the driver&#39;s seat is arranged at a lower position, the deflection means is deflected to a lesser extent than if the driver&#39;s seat is in its upper position, and as a result the segment has a greater incline to the horizontal and hence the deflection means has a greater deflection. 
         [0012]    Advantageously the active connection is located at a distance from at least one of the arrangement areas. 
         [0013]    In a preferred embodiment of the present invention, between a first rotary point of a segment of the scissors-type frame and a plane of the arrangement area is a first distance which is greater than a second distance of a further rotary point of a segment of the scissors-type frame from a plane of the corresponding arrangement area. This embodiment is advantageous since it gives different distances due to connections arranged on different planes between the segments of the scissors-type frame and individual mountings. This leads at least partly to a vibration decoupling between for example the upper and the lower arrangement area. 
         [0014]    In one application of the device to vehicle seats, the upper arrangement area corresponds to an upper seat area and the lower arrangement area corresponds to a lower seat area. The lower arrangement area or lower seat area is attached to the vehicle and the upper arrangement area or upper seat area is movable in relation to the vehicle at least in the vehicle height direction corresponding to the seat height direction. 
         [0015]    The spring system is also attached to the vehicle when it is arranged or used between a vehicle cab and the vehicle or vehicle frame. In such an embodiment the vehicle cab can be displaced in the vehicle height direction in relation to the vehicle frame or vehicle. 
         [0016]    Also combined arrangements are conceivable in which the cab is movable in the height direction and on or in the cab a seat fitted with a spring system is provided which is also movable in the vehicle height direction. 
         [0017]    It is also conceivable for the deflection means and spring element to be coupled in such a way that the connection point is provided variably on the deflection means and can be fixed in any position as required. The closer the connection point lies to the corresponding arrangement area, the higher the possible moment that can be transmitted by the spring element to the scissors-type frame for the same spring force. 
         [0018]    In a further preferred embodiment of the present invention, in a first operating state the deflection of the deflection means causes a deflection of the scissors-type frame. This is advantageous as the scissors-type frame can be modified by the deflection of the deflection means. It is also conceivable that the deflecting means is deflected by deflection of the scissors-type frame. 
         [0019]    In a further preferred embodiment of the present invention, at least one segment of the scissors-type frame has a first section that is shorter than a second section of the segment. This is advantageous as also at least partly a vibration decoupling is possible of the vibrations from the individual segment sections on the basis of different resonance sections. Furthermore such an arrangement causes different forces because of the different lever ratios on the different mountings. This is advantageous as, depending on the alignment of the spring system, the desired or required forces can be provided for the application of force to the spring element. 
         [0020]    In a further preferred embodiment of the present invention, on deflection of the scissors-type frame the maximum deflection of the connection point is preferably less than the maximum deflection of the first section of the segment of the scissors-type frame and particularly preferably the maximum deflection of the connection point is smaller than the maximum deflection of the second section of the segment of the scissors-type frame. This is advantageous as despite the relatively great deflection of the entire system, a substantially smaller deflection of the spring element is possible. It is therefore possible for example to provide a comparatively small or short spring element. The term deflection here means the maximum travel covered by the section which moved fastest, in terms of angular speed, of the first or second section of the segment of the scissors-type frame or connection point. 
         [0021]    In a further preferred embodiment of the present invention, in the first operating state the deflection means is connected with the scissors-type frame and locked in relation to this. This embodiment is advantageous as in this configuration the forces of the spring element can be transmitted via the deflection means to the scissors-type frame or vice versa. A further embodiment is also conceivable in which the deflection means and scissors-type frame are formed as one piece, whereby admittedly no adjustment of the spring force is possible but lower production costs can be achieved. The term “one piece” in this case also includes components connected together non-releasably i.e. by welding connected parts. 
         [0022]    In a further preferred embodiment of the present invention, between the segment of the scissors-type frame and a straight line defined by a mounting point at which the deflection means is in contact with the segment of the scissors-type frame and the connecting point is a fixed angle in the locked state. 
         [0023]    This embodiment is advantageous as the angle between the straight line and the scissors-type frame in the locked state cannot be changed and hence in the first operating state no undesirable spring force adjustments can take place. 
         [0024]    In a further preferred embodiment of the present invention, in a second operating state the deflection means can be moved in relation to the scissors-type frame from a first locked position to a second locked position. This is advantageous as changing the position of the deflection means allows a change or adjustment of the spring force. The position of the deflection means can be set and/or fixed or locked arbitrarily in relation to the lever element. Also it is conceivable and advantageous that for a constant lever ratio i.e. a constant distance between the applied spring force and the point about which the moment acts, a change of spring force is possible. 
         [0025]    In a further preferred embodiment of the present invention the deflection means is connected with a lever element, wherein the lever element can be designed as a rod and plate, hollow, of solid material and with any cross section e.g. round, rectangular, polygonal etc. The lever element is furthermore rotatably connected with an element which is also rotatably connected with the segment of the scissors-type frame. 
         [0026]    This embodiment is advantageous as due to the lever ratios occurring, a deflection of the scissors-type frame in the height direction is again possible which is greater than the deflection of the spring element. 
         [0027]    Furthermore it is advantageous that due to the arrangement described above, a connection exists between the lever element, the deflection means and the segment of the scissors-type frame. The further element rotatably connected with the scissors-type frame allows an interaction of these components without stresses occurring in the system. Preferably the further element is also connected rotatably with the lever element. Here however it is also conceivable that in a first operating state, the deflection means is fixed in relation to the lever element i.e. the movement of the lever element causes a deflection of the deflection means and vice versa. The deflection means in a second operating state is also preferably movable in relation to the lever element i.e. can be moved from a first fixed or locked position to a further fixed or locked position. In a further embodiment the deflection means and lever element are formed as one piece, wherein the term “one piece” should also be understood as non-releasable in the sense discussed above. 
         [0028]    In a further preferred embodiment of the present invention, the lever element and deflection means are arranged rotatably about an axis. This axis is spaced from any further axis about which at least one segment of the scissors-type frame is arranged rotatably. This is advantageous as the deflection means does not act on or is not arranged directly on a segment of the scissors-type frame but through the lever element, any arbitrary position at the respective segment of the scissors-type frame can be assumed for the application or reception of force. Due to the length of the lever element and spring element therefore widely differing force and lever conditions can be expected. 
         [0029]    In a further preferred embodiment of the present invention, a second end of the spring element is arranged on a segment of the scissors-type frame, the upper or the lower arrangement area or the vehicle frame. This is advantageous as the spring element, on displacement of the upper arrangement area in the height direction, can also be moved fully in the height direction or the spring element can be deflected merely in its length and swiveled about an axis at the point of attachment of its second end. 
         [0030]    In a further preferred embodiment of the present invention, the spring element is arranged preferably horizontally between the segments of the scissors-type frame. This is advantageous as the spring element is arranged protectedly i.e. for example surrounded or enclosed by the upper part of a vehicle seat. The spring element can here preferably be designed as a gas spring, a plastic spring, a rubber spring, a metal spring such as e.g. a coil spring, a torsion spring, a leg spring or a combination of these or further spring elements. 
         [0031]    In a further preferred embodiment of the present invention, the deflection means can be operated and/or fixed or locked manually, mechanically, electrically, pneumatically or hydraulically. This is advantageous since the suitable operation mode or suitable combination of these operating modes can be provided for locking and operation, i.e. a change of position of the deflection means depending on the manner of use of the device, comfort requirement and available energy supply system. 
         [0032]    In a further preferred embodiment of the present invention, the deflection means is formed plate-like at least in sections and/or preferably in sections rod-like and particularly preferably lever-like. This is advantageous as such plate-like and/or rod-like and lever-like means are simple, accurate and economic to produce. 
         [0033]    Further preferred embodiments arise from the sub claims. 
         [0034]    The benefits and suitabilities are described in the description below in conjunction with the drawings. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0035]    These show: 
           [0036]      FIG. 1  an extended state of the scissors-type frame with a deflection means provided on the scissors-type frame and shown in a first configuration; 
           [0037]      FIG. 2  a retracted state of the scissors-type frame and a deflection element which is also arranged on the scissors-type element and has the same angle to the scissors-type element as is the case in  FIG. 1 ; 
           [0038]      FIG. 3  an extended position of the scissors-type frame with a deflection means arranged on the scissors-type frame and shown in a further configuration; 
           [0039]      FIG. 4  an arrangement showing the deflection means in a further configuration in comparison with  FIG. 2 ; 
           [0040]      FIG. 5  a scissors-type frame and a deflection means which is mounted at a distance from the scissors-type frame; 
           [0041]      FIG. 6  the device known from  FIG. 5  in a further configuration; and 
           [0042]      FIG. 7  in a graph, the force-travel curves for the device according to the invention. 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       [0043]      FIG. 1  shows a diagrammatic view of a lower section of a vehicle seat or a vehicle cab of a vehicle, wherein the spring system  101  can be set to oscillate in the vertical direction. The spring system  101  has an upper arrangement area  102  and a lower arrangement area  104  which are connected together via a scissors-type frame  106 . The scissors-type frame  106  comprises a first segment  108  and a second segment  110  that are connected together via a central axis  111 . 
         [0044]      FIG. 1  shows that the first segment  108  has a first section  112  that is longer than a second section  114 . It is however also conceivable that the second section  114  is longer than the first section  112  or the two sections  112 ,  114  are the same length. 
         [0045]    The first segment  108  has a first axis  116  that can be displaced in the x-direction. It is conceivable that a wheel is provided on the first axis  116  mounted movable in the lower bearing  117  or a slide element is provided on the first axis  114  mounted sliding in the lower bearing  117 . The second axis  118  and upper bearing  119  for example can also be produced corresponding to the statements on the first axis  116  and the lower bearing  117 . 
         [0046]    The second segment  110  is mounted next to bearing  119  and rotatable about a third axis  120  in a lower rotary bearing  122  that is provided on the lower arrangement area  104 . The first segment  108  in the upper arrangement area  102  is mounted about a fourth axis  124  provided in an upper rotary bearing  126 . The upper rotary bearing  126  is formed longer in the height direction h than for example the lower rotary bearing  122 , whereby the fourth axis  124  is spaced further from a plane of the upper arrangement area  102  than the second axis  118 . Also the deflection means  128  is arranged rotatable about the fourth axis  124  and is movable from a first position fixed in relation to the first segment  108  into a second position fixed in relation to the first segment  108 . 
         [0047]    On the deflection means  128  shown as a lever in  FIG. 1  a spring element  130  is mounted at a connection point  132 . The second end  134  of the spring element  130  is attached according to the depiction in  FIG. 1  on the second segment  110  of the scissors-type frame  106 , wherein the second end  134  of the spring element  130  can also be attached to the upper arrangement area  102 . The second end  134  of the spring element  130  is preferably mounted rotatable, it is however also conceivable that the second end  134  of the spring element  130  is firmly clamped. 
         [0048]      FIG. 2  shows a spring system  201  in a position of minimised or reduced height. In this position the upper arrangement area  202  is physically very close to the lower arrangement area  204 . The scissors-type frame  206  therefore in comparison with the scissors-type frame in  FIG. 1  extends less in the height direction h but further in direction x. Because of the modified position of the device  206  in relation to  FIG. 1 , the first segment  208  of the scissors-type frame  206  and the deflection means  228  can be rotated about the fourth axis  224  at a constant angle, whereby the spring element  230  is deflected in the x-direction. 
         [0049]      FIG. 3  shows the scissors-type frame  306  according to the positioning known from  FIG. 1 , wherein the angle between the first segment  308  of the scissors-type frame  306  and the deflection means  328  changes from the position shown in  FIG. 1  i.e. is more acute. The deflection means  328  is thus rotated about the fourth axis  324  such that the connecting point  332  at which the spring element  330  is connected with the deflection means  328  causes a compression or release of the spring element  330 . 
         [0050]      FIG. 3  and  FIG. 4  show different height positions of the vehicle seat which are characterised by different deflections of the deflection means in relation to the segment of the scissors-type frame. For example the deflection means  328  can be deliberately modified in position in a lowered position of the vehicle seat as shown in  FIG. 4  in order to achieve a different angle α between the extent of the deflection means  428  and the segment  408  of the scissors-type frame. This has the effect that the spring element  430  receives a stronger force and hence a greater effect can be achieved in the vibration reduction of the entire vehicle seat. 
         [0051]      FIG. 4  shows a further depiction of a spring system  401  in a lowered height configuration. In comparison with the view shown in  FIG. 2 , the lever  428  is rotated about the axis  424  such that the angle between the first segment  408  of the scissors-type frame  406  and the deflection means  428  is greater. Due to this greater angle between the first segment  408  and the deflection means  428 , the spring element  430  is deflected more in comparison with the spring element  230  known from  FIG. 2 , whereby the spring element  430  shown in  FIG. 4  exerts a different force from the spring element  230  shown in  FIG. 2 . 
         [0052]      FIG. 5  shows a further embodiment of a spring system  501 , where at the lower arrangement area  504  is mounted a lower rotary bearing  522  in which the scissors-type element  506  is mounted merely rotatably. The upper rotary bearing  526  as in  FIG. 4  is also formed longer in height direction h than for example the lower rotary bearing  522 , wherein it is conceivable that the upper rotary bearing  526  can also be produced in the same length as the lower rotary bearing  522 . Furthermore it is conceivable that the lower rotary bearing  522  is formed longer than the upper rotary bearing  526 . 
         [0053]    Arranged on the deflection means  528  is a spring element  530  at a connecting point  532 . The spring element  530  furthermore has a second end  534  which is mounted preferably rotatably in a holder  548  of the spring element  530 . The holder  548  of the spring element  530  is in a further bearing  546  connected with the lower arrangement area  504 . In comparison with the arrangement of the other bearings, the further bearing  546  is arranged in the horizontal direction, wherein an arrangement of the further bearing  546  in the vertical direction is also conceivable, where the other bearings can also be arranged horizontally accordingly. 
         [0054]    The deflection means  528  can be rotated about a fifth axis  536  provided by a bearing of the deflection means  537 . Also arranged rotatably on the fifth axis  536  is the lever element  538 . The deflection means  528  and the lever element  538  are actively connected with each other i.e. the angle included between them can be modified. It is also conceivable that the angle between the lever element  538  and the deflection means  528  is fixed, as the deflection means  528  can also be connected non-releasably with the lever element  548 . 
         [0055]    Arranged on the lever element  548  is a sixth axis  540  about which can be rotated a further element  542  that is rotatably connected by means of a seventh axis  544  with the second segment  510 . A force application in the spring system  501  via the upper arrangement area  502  or the lower arrangement area  504  which leads to a change of distance between the upper arrangement area  502  and the lower arrangement area  504 , at the same time causes a change in length of the spring element  513  or vice versa. 
         [0056]      FIG. 6  shows in comparison with  FIG. 5  a modified height h of the spring system  601  whereby it is clear that a length change of the spring element  630  has occurred. It is also clear from  FIG. 6  that in comparison with  FIG. 5 , a provided or theoretical line at right angles from the second segment  610  into the centre of the fifth axis  636  is longer than is the case in  FIG. 5 . Furthermore in  FIG. 6  an arranged or theoretical line at right angles on the second segment  610 , protruding into the centre of the sixth axis  640 , is shorter than is the case in  FIG. 5 . 
         [0057]      FIG. 7  depicts in a graph a force-travel curve for drivers of different weights using a vehicle seat with the spring system according to the invention. The ordinate shows the spring force of the spring system and the abscissa the associated travel of the spring system in the height direction. A driver with a low weight produces curve  700  with a load spring force  701  in relation to the associated vibration travel. Such a light-weight driver also experiences as good a vibration reduction as a heavy driver, whose curve is shown marked  702  with associated spring force  703 . 
         [0058]    Because of the modified deflection of the spring element which is achieved by the differently positioned deflection means as a function of the momentary position of the scissors-type frame, a different spring force is obtained with reference numerals  701  and  703  as a function of the driver&#39;s weight. A strong compression of the spring system with associated seat would generate a strong counter spring force according to numeral  703 , where in contrast a weaker extension/compression would provoke a weaker counter spring force  701 . 
         [0059]    The spring characteristics  700  and  702  have different gradients as a function of the weight of the driver and the counter spring force provoked, wherein the gradients are arranged at different angles  704  to the horizontal. Both the angle size and the mass m of the driver are used in a vibration frequency formula 
         [0000]    
       
         
           
             f 
             = 
             
               
                 1 
                 
                   2 
                    
                   π 
                 
               
                
               
                 
                   
                     m 
                     
                       C 
                       s 
                     
                   
                 
                 . 
               
             
           
         
       
     
         [0000]    The mutual dependency of the mass of the driver and the angular deflection of the characteristics gradient are shown according to this formula. This shows that good vibration reduction is possible both for a lightweight and a heavyweight driver. 
         [0060]    All features disclosed in the application documents are claimed as essential to the invention where novel individually or in combination in relation to the prior art. 
       LIST OF REFERENCE NUMERALS 
       [0000]    
       
           101 ,  201 ,  301 ,  401 ,  501 ,  601  spring system 
           102 ,  202 ,  502  upper arrangement area 
           104 ,  204 ,  504 ,  604  lower arrangement area 
           106 ,  206 ,  306 ,  406 ,  506 ,  606  scissors-type frame 
           108 ,  208 ,  308 ,  408  first segment of scissors-type frame 
           110 ,  210 ,  510 ,  610  second segment of scissors-type frame 
           111  centre axis 
           112  first section of segment 
           114  second section of segment 
           116 ,  216  first axis 
           117 ,  217  lower plain bearing/roller bearing 
           118 ,  218  second axis 
           119 ,  219  upper plain bearing/roller bearing 
           120 ,  520 ,  620  third axis/second rotation point/application point 
           122 ,  522 ,  622  lower rotary bearing 
           124 ,  224 ,  324 ,  424 ,  524 ,  624  fourth axis/first rotation point/application point 
           126 ,  226 ,  326 ,  426 ,  526 ,  626  upper rotary bearing 
           128 ,  228 ,  328 ,  428 ,  528 ,  628  deflection means/lever 
           130 ,  230 ,  330 ,  430 ,  530 ,  630  spring element 
           132 ,  232 ,  332 ,  432 ,  532  connection point 
           134 ,  534  second end of spring element 
           536 ,  636  fifth axis 
           537  bearing of deflection means 
           538 ,  638  lever element 
           540 ,  640  sixth axis 
           542 ,  642  further element 
           544 ,  644  seventh axis 
           546 ,  646  further bearing 
           548 ,  648  holder of spring element 
           700 ,  702  curve 
           701 ,  703  spring force 
           704  different angle