• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    An improved counterbalance hinge assembly has a bias spring and uniquely shaped cam for counterbalancing inherently nonlinear forces represented by pivoting loads such as fold up wall type beds, desks, and the like. A cable attached to the spring wraps progressively around the cam surface as the bed or other load is pulled out from the wall, thereby compressing the spring. The effective radius of the cam at a given point is designed in conjunction with the peripheral extent of the cam surface up to that point, to give the desired counterbalancing force as a function of the angular position of the load. In the preferred embodiment, the effective radius is thus smaller with the bed in its horizontal position than with the bed in its vertical position. Additionally, a small offset angle may be provided in the counterbalancing mechanism near the vertical position, to aid in moving the load to and from its stored position.
    公开号:SU733522A3
    申请号:SU762375461
    申请日:1976-06-24
    公开日:1980-05-05
    发明作者:Конрад Буи Ричард；Лерой Горсак Филлип
    申请人:Сайко Инкорпорейтед (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to the field of mechanical engineering, in particular, to balancing hinge devices of folding furniture parts. A hinged connection for folding folding furniture is known, comprising a fixed bracket and a hingedly movable bracket for connecting it with a folding part, which are interconnected by means of a cable and prejudges with preliminary effort ij. In such a connection, the balancing spring is provided with a cable that is wound on the drum, combined with the point of rotation of the load, while the working surface of the drum is shaped like a cylinder. However, the operating conditions of the known construction are complicated in view of the need to install additional balancing springs in order to facilitate the movement of the folding furniture part from the working position to the storage position and to achieve the necessary balancing ability of the joint. The purpose of the invention is to improve the operating conditions of the compound. The goal is achieved in that the hinge connection for the folding furniture parts, comprising a fixed bracket and a hingedly movable bracket associated with it for connecting with the folding component, which are interconnected by means of a cable and a spring with a preliminary adjustable force, is provided with a cam mounted on one of the these brackets, one end of the spring is directly connected to the bracket on which the cam is mounted, and the other end of the spring is connected with the HELP cable with the other bracket, while Ocha cam surface, cooperating with the cable, limited radii of different sizes, the largest of which faces the bracket zannomu communication with the cam, and a lower arm to the other, on which is mounted a cam. Here, the cam is attached to the movable bracket, and the end of the spring is directly connected to the fixed bracket. The cam can also be mounted on a fixed krsn111t pch :,
    and the end of the spring is directly connected to the movable bracket.
    In addition, the cam working surface is made according to a variable radius determined from the following relation t - i qKs: nd,
    where r is the cam profile radius
    defined point;
    f - spring deformation;
    P - spring stiffness; Q is the weight of the movable part of the compound;
    .R is the distance from the center of the sheet metal to the center of its rotation;
     - the angle of deviation of the center of gravity of the movable part from the vertical.
    Figure 1 shows the described hinge connection in a perspective view in figure 2 the same, front view; on fig.Z - the same, side view, with a partial section; Fig. 4 shows the part in a vertical position; Fig. 3 is a diagram illustrating the movement of elements in the described connection from a vertical to a horizontal position; in fig. cam.
    The hinge consists of a fixed 1 and a movable 2 brackets, which are connected with the possibility of rotation with a finger 3. The bracket is adapted for rigid attachment to the floor or to Any flat reinforcing element that can be mounted on the floor. It has pivotal: fencing enclosures 4 for reinforcing and imparting greater stiffness and horizontal flange sections 5, which are used for fastening the hinge to the floor with the help of nut and bolts b. The bracket 1 includes a vertical end plate 7 and the corresponding straps 8, which interconnect the flange portion 5 and the vertical end plate 7. The bracket 1 may, depending on requirements, be cast or welded from individual corner pieces.
    At the front end of the bracket 1, a step 9 is provided, which in the described construction is shown parallel to the floor, but located at some distance from it. A pair of guide plates 10, 11 is welded to the step section 9. Directly, the plates 10, 11 are installed vertically and are spaced apart from each other with the possibility of placing the cam 12. The finger 3 passes through; the guide plates 10, 11 and The hole is bore: provided in the cam 12, ensuring its free rotation.
    The movable arm 2 is that part of the hinge comprising the cam 12, which rotates with a flip part or other load around the finger 3. The movable arm 2 has a pair of angles 13,14 that are welded to the side surfaces of the cam 12. If necessary, the cam 12 and angles 13,14 can be made from a single casting.
    The hinge frame 15 of the furniture is bolted to the corners 13,14 of the movable arm 2. The panel 16 can be attached to the bottom of the hinged piece 15. If the device is installed in a small niche, the panel 16 will close the niche, creating a surface adjacent to the wall. Other furniture items are attached to the frame of the flip-down part 15 for rotation with it.
    The design provides a locking element, made the bolt 17, screwed into the threaded hole angle. When the part 15 is moved to a vertical position, the head 18 of the bolt 17 rests on the step section 9 of the fixed bracket 1 (the drawing of the drawing is shown by dashed lines). This is necessary to limit the vertical movement of the part 15. The stopper is adjusted by rotating the head 18 of the bolt 1 and the lock nut 19 is used to fix the stopper in the desired position.
    权利要求:
    Claims (4)
    [1]
    On the cylindrical spring housing 20 there is a pair of anchor bolts 21 welded to its outer surface to secure the spring housing to the fixed bracket 1 and to ensure its adjustment. Anchor bolts pass through the holes provided in the vertical end plate 7 and are secured with nuts 22 and spherical washers 23 which allow a slight change in the position of the spring housing. A spiral spring 24 is located inside the spring housing. One end of the spring rests on the blind end of the housing 20 and the other is connected to the washer 25. On the bearing surface of the washer 25 there is a cylindrical reinforcing element 26, which is rigidly connected to it. Element 26 serves to reinforce the washer 25, as well as to restrict movement and determine the position of the washer relative to the spring 24, since the outer diameter of the reinforcing element 26 is chosen to be slightly smaller than the inner diameter of the spring 24. The cable 27 passes inside the spring 24 and the central hole 28 at the end of the spring housing. Further, the cable 27 passes through the cam 12, and the other end of it is attached to the movable bracket with the help of the cable retainer 29, which is fastened to the corresponding protrusion 30 located in the edge of the cam 12. The cable is guided along the surface of the cam 12 using the angles 13, 14, located on both sides of the cam. When the tilting part is in a horizontal position, the cable 27 is pulled around the cam 12, forcing the washer 25 to compress the spring 24. In this position, the spring 24 creates a balancing moment about axis 3, which is determined by the degree of movement or compression of the spring 24 and the effective radius at the point contact, determined by the distance from the point of contact 31 of the cable to the center of rotation of the finger 3. When the part 15 is moved to a vertical position, the cam 12 rotates counter-clockwise, allowing the spring 24 to reduce its contraction. When part 15 is located near the top of its path, the spring applies its counterbalancing force on the effective radius determined by the distance from the point 3 of the cable touch to the center of rotation of the foot 3. The effective radius at the point of contact (at the horizontal position of the part 15) is shorter, than the effective radius at the point of 32 contacts (in the vertical position). With the total amount of movement or compression of the spring 24, determined by the size of the path of the washer 25 when the spring is compressed, is equal to the total length of the path along the periphery of the cam surface from point 31 to point 32, numerous variations in the overall size and type of cam and shape of the hinge are possible in the present invention. For example, if necessary, it is possible to install two or more springs acting in parallel, instead of one spring shown in the drawing. It is also possible to swap the cam and the spring so that the spring is connected to the moving part of the frame, while the cam would be attached to the fixed part. In any case, the principle of operation remains the same. The required torque, which must be applied relative to the center of rotation in order to balance the load in the hinge joint, can be defined as UTkSW l. where W is the bed weight; X is the distance from the center of rotation to the center of the bed sheet; t is the angle made up by the bed with the wall. Thus, the required balancing moment increases as the bed is pulled away from these walls. The force created by the spring is Sd, where S is the coefficient of elasticity of the spring, d is the displacement (both compression and tension; springs. The balancing torque created by the spring is equal to the force of the spring multiplied by the effective radius g (d) The important point is that the movement of the spring 24 is also a function of the angular position of the part 15 and the effective peripheral length of the path along the cam surface from the starting point of contact to the desired point. In general, the effective radius r (d) is equal to the distance from the center of rotation to the point of contact of the cable, and the movement d (d) is equal to the circumferential length of the path, which means that (d) (d) 5ShdS using the above equation, the cam can be calculated using a sequential approximation method. For a selected weight of the load to the spring coefficient, the desired radius of the cam can be calculated at the first design point, for example 10 ° from the vertical position. The radius can be roughly calculated by the following calculated point, for example, 20 °. The resulting circumference can be determined graphically, and based on this, it is necessary to recalculate the radius at the second design point. This, in turn, will affect the length of the circle, which must be redefined. Each subsequent approximation brings closer and closer values to exact values, and after several such steps, exact values can be determined with any desired degree of accuracy. This procedure is then repeated for each subsequent calculation point on the cam surface. Although the drawings show only one hinge device, in practice, usually a pair of similar devices is required for the chosen design, and the balancing effect of both devices should be taken into account when calculating the need for spring parameters or other calculated values. An additional factor that must be taken into account when calculating the hinge device is that in many cases it is necessary to open the center of rotation relatively close to the floor and near the decorative panel 16. Thus, with applied loads, the center of gravity of the load tends to fall to the left of the vertical line. passing through the center of rotation of the hinge. The weight of the load, which is somewhat behind the center of rotation, serves to bring the part 15 to the storage position (vertical), without the need for various latches. If the part 15 is required to be moved to a horizontal position, the operator must initially open its center of gravity. Therefore, it is necessary that the balancing spring, which usually tends to push the bed to the wall, does not take effect until this initial part of the path of the part 15 is passed. For this, an initial balance angle is provided for the hinge joint. Line 33 depicts the balance position of the part 15, in which the center of gravity of the part is located at a point above the hinge axis of the finger 3 and the balance angle is the angle between the line 33 and the vertical. In conventional settings, the balance angle can be approximately 10. depending on the design of the part 15, the once calculated angular relation between the cam and the movable arm 2 is then adjusted accordingly during the manufacturing process. Thus, the cam 12 is out of phase with respect to the part 15 by an angle equal to the balanced angle. The cam 12 is in its original position, or position o, with respect to the contact of the cable 27 while the part 15 is in the balanced position 34. The surface of the panel of the part 1 that is installed in another way advances the cam by the balance angle and the cam is in the zero position when Sheet part 1 is located vertically above the center of rotation. If the center of gravity moves 15 or another load, for example, by adding a heavy mirror to the decorative panel, it is theoretically necessary to change the angular relationship between the cam 12 and the part 15 in order to reflect the change in the balance angle. However, for the design described, it is characteristic that in practice it is possible to adjust the relatively large change in the position of the effective center of gravity of the load by simply adjusting the nuts 22, which ultimately move the spring housing to the right and left as necessary. By changing the weight of the part 15 or the load, in order to compensate for this change, the coefficient of elasticity of the spring can be changed. Since this is easy to implement, such a hinge connection can & a have been used in various bed models with different weights. And for unintended large changes in bed weight, for example, caused by the addition of a mirror or other accessories, the effect of additional weight can be sufficiently compensated for by additional adjustment of the nuts 22. In practice, the reclining furniture 15 is horizontal and then the position of the spring casing is adjusted. creating the required drop weight. This ensures that part 15 (for example, a bed) will remain down if it is required to be in the working position. After that, it is sufficiently balanced in the entire range, despite the fact that the adjustment can cause the spring to be activated a few degrees before or after the balance position. Such a slight overshoot does not impair the balancing capacity of the hinge, but allows adjustment with a wide variety of weights of loads and positions of the centers of gravity. It is also necessary to take into account the fact that the system is designed in such a way that the force of the spring decreases to zero in the position of the balance angle; Further movement of the part 15 to the storage position or vertical position causes the cable to loosen. However, when tilting the part 15, the slack is selected when the part approaches its balance point depending on the fineness of adjusting the nuts 22. While the equation and calculation procedure described above results in a balancing hinge that is completely balanced the paths of movement of the part 15 from a balanced position to a horizontal one, in practice, the cam profile may be somewhat modified relative to the cam profile calculated for perfect balance. So, in the preferred & version of the cam is designed this way. in order to completely balance the part in the average angular range, approximately from 20 to 65, However, from a point of 0 ° on the cam (point 32) applied to 20 a cam can have a slightly smaller radius than the one that is required for perfect balance. This creates a definite advantage, since once the balanced part 15, the part 15 itself will slowly begin to fall; but will stop when it reaches the middle section of full balance. Moreover, when the part 15 rises to a vertical position, a smaller than required equilibrium in the area from 0 to 20 will help to slow down the acceleration of part 15 caused before this lifting movement so that its movement slows down and it hits the wall. Approximately 65 to the end of the cam, respectively, when the part 15 is in a horizontal or near position, it may be clearly necessary to provide a slight decrease in radius in order to create a slightly smaller than the full counterbalancing force. This allows for the guaranteed retention of the part 15 in a horizontal position: Neo, it should be borne in mind that these areas of the corners are only approximate and can be changed if necessary. The amount by which the radius can be reduced in these areas can vary according to the desired effect of the effects noted above. Although this small decrease in cam radius in the two zones theoretically affects the circumference of the cam leg,, in practice, the necessary radius decreases are very small and it has been found that the effect of changing the circumference length is insignificant, and thus the calculation procedure simplifies with . An example. An embodiment of the invention is made (see drawings) with a cam having a radius value according to the following table. Radius, Cam angle, mm 63.3 degrees. 66.0 66.5 66.0 62.0 62.0 58.5 54.1 49 .. 8 The values given above correspond to a modified construction, in which perfect balance is realized in the middle region, and is less than perfect Equilibrium is created when the flip-down piece of furniture is near its horizontal and vertical positions in order to facilitate the rotation of the piece, as described above. The angles in the table below correspond to the corner positions of the cam, and the point O corresponds to the point 32 of the touch on the cam. In this example, a ten-degree balance angle of the part 15 is taken. The value for the 90 ° position of the cam was not calculated, because the position of the cam corresponds to the horizontal position of the part 15 "The invention allows to significantly improve the operating conditions of the hinge connection f increases its compactness, eliminates the need to install additional compensatory devices. Claim 1. Hinged connection for folding furniture parts, comprising a fixed bracket and a hingedly movable bracket connected to it for connecting with a folding part, which are interconnected by means of a cable and a spring with a preliminary angle of one or more v1, characterized by the fact that in order to improve its operating conditions, it is equipped with a cam mounted on one of these brackets, one end of the spring is directly connected to the bracket on which the cam is mounted, and the other end of the spring A cable is connected with a cable and is limited to radii of various sizes, the smaller of which is facing the bracket on which the cam is fixed and the larger to the other bracket.
    [2]
    2. A hinge connection according to claim 1, characterized in that the cam is fixed to the movable bracket, and the end of the spring is directly connected to the fixed bracket.
    [3]
    3. A hinge connection according to claim 1, characterized in that the cam is fixed on the fixed bracket, and the end of the spring is directly connected to the movable bracket.
    [4]
    4. A hinge joint according to claims 1 to 3, characterized by by the fact that the cam working surface is made in a variable radius, on the basis of the following ratio; .i-iiisi-,
      cam profile radius at a defined point;
    f - spring deformation;
    ll spring stiffness;
    Q, is the weight of the movable part of the joint;
    R is the distance from the center of gravity of the moving part to
    the center of its rotation; d is the angle of deviation of the center of gravity of the moving part from the vertical.
    Sources of information taken into account in the examination 1. Patent of France W 710157, gr.9 KL.4, 1931.
    FLG,
    类似技术:
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    SU733522A3|1980-05-05|Articulation joint of hinged furniture parts
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    同族专利:
    公开号 | 公开日
    EG12530A|1979-03-31|
    MX142998A|1981-02-04|
    FR2317544B1|1978-05-19|
    DD126017A1|1977-06-08|
    NZ180376A|1978-06-20|
    HK66079A|1979-09-21|
    IN155941B|1985-03-23|
    DK148464B|1985-07-15|
    DE2613133B2|1977-09-15|
    TR18989A|1978-01-01|
    US3999245A|1976-12-28|
    RO81003A|1984-07-17|
    IT1058696B|1982-05-10|
    JPS529762A|1977-01-25|
    BR7603709A|1977-01-18|
    JPS5342862B2|1978-11-15|
    USB594871I5|1976-03-16|
    PH12826A|1979-08-31|
    YU40454B|1986-02-28|
    DK148464C|1985-12-16|
    FR2317544A1|1977-02-04|
    DE2613133C3|1978-05-18|
    AR211017A1|1977-10-14|
    GB1543251A|1979-03-28|
    CH607901A5|1978-12-15|
    ES447092A1|1977-09-16|
    PL111539B1|1980-09-30|
    CA1031912A|1978-05-30|
    DE2613133A1|1977-01-20|
    DK276776A|1977-01-11|
    AU1389076A|1977-11-17|
    RO81003B|1984-09-30|
    YU91776A|1982-05-31|
    DE7609498U1|1977-07-21|
    MY8000145A|1980-12-31|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    RU192088U1|2019-05-13|2019-09-03|Акционерное общество "Ульяновский механический завод"|Lockable swivel assembly|FR710157A|1931-01-30|1931-08-19|Device applicable to box springs, daybeds or sleeping beds|
    US2779032A|1953-02-16|1957-01-29|Pullman Standard Car Mfg Co|Folding bed counterbalance mechanism|
    US3550167A|1968-02-28|1970-12-29|Hilliard D Bennett|Wall bed structure|
    US3828375A|1972-11-24|1974-08-13|W Driver|Storable beds|US4337670A|1979-10-02|1982-07-06|Sico Incorporated|Yieldable multi-function linkage apparatus for powered pivoting loads|
    US4601446A|1983-09-29|1986-07-22|The Boeing Company|Aircraft door counterbalance system|
    US5446932A|1994-05-18|1995-09-05|Voorhis; Donald P.|Folding wall bed|
    US5978988A|1997-12-18|1999-11-09|C.A.B., Inc.|Frame for pivoting folding furniture having varying counterbalancing torque values|
    FR2787476B1|1998-12-22|2001-03-02|Barat Sa|IMPROVEMENTS IN OR RELATING TO A LOCKING DEVICE FOR AN ACCESS TRAP OF GALLERIES AND UNDERGROUND WORKS OF CIVIL ENGINEERING, CONSISTING OF AT LEAST ONE LEAF|
    SG99938A1|2001-08-07|2003-11-27|Sico Inc|Folding bed|
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    US7611193B2|2006-04-18|2009-11-03|Sico Incorporated|Table and seating arrangement|
    US7712422B2|2006-07-19|2010-05-11|Sico Incorporated|Folding table|
    US7793366B2|2006-08-29|2010-09-14|Nathan Lee Stoltzfus|Combined wall treatment and bed|
    US8820826B2|2009-09-10|2014-09-02|Sico Incorporated|Table and seating apparatus|
    US8182032B2|2009-09-10|2012-05-22|Sico Incorporated|Table and seating apparatus|
    JP6307437B2|2012-11-14|2018-04-04|アダマンド並木精密宝石株式会社|Tubing pump|
    DE102015102393A1|2015-02-19|2016-08-25|Hettich Holding Gmbh & Co. Ohg|swivel fitting|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US05/594,871|US3999245A|1975-07-10|1975-07-10|Counterbalance hinge for pivoting loads|
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