FI122528B - Device for balancing a body moving in a vertical plane back and forth along a circular path - Google Patents

Description

HORIZONTAL PLANNING EQUIPMENT FOR BALANCING A MOVABLE MOVEMENT BACK

The invention relates to an apparatus, as defined in the preamble of claim 1, for balancing a body to be moved in a vertical plane along a circular path or other closed path.

The torque variable balancing apparatus according to the invention is suitable for many different applications. For example, it may be a balancing mechanism for a traffic boom or equally well may be used to balance a substantially vertical motion of any substantially articulated object at one end or edge with the center of gravity of the object moving along a substantially closed circular path. Such pieces include, in addition to booms, skylights, hatches, tilt doors, car hoods, tailgates, machine-operated levers and associated masses, as well as lifting bridges and similar structures.

For example, a counterbalance known in the art as the balancing movement of a movement of a vertically movable member hinged at one end or at an edge, including a counterweight, is caused by a moment corresponding to a variable moment caused by the position of a moving body. However, the problem with the counterweight is its weight and> the space it requires. Usually, the counterweight cannot be used as an example to balance the bonnet and tailgate of the cars, owing to the lack of counterweight in the car's structures.

Similarly, at the ends of traffic booms or similar booms, there is usually no space for such a counterweight as the solution

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gj would insist. For this reason, a counterweight boom solution 30 su is currently not in general use.

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European Patent No. EP0438364 B1 and US Patent No. 4,848,175 disclose solutions for balancing the movement of a traffic boom. Both patents disclose a complex apparatus based on levers and springs with a large number of different small parts. The problem with these is, among other things, the high number of parts, which reduces the reliability of operations and increases costs. In addition, booms come in many different sizes and variations, so each size and variation must have its own dimensions. This significantly increases the number of parts needed, including storage costs are increasing.

The object of the present invention is to eliminate the above drawbacks and to provide an inexpensive, reliable and energy saving apparatus for balancing a reciprocating body along a closed path. The apparatus according to the invention is characterized by what is set forth in the characterizing part of claim 1. Other embodiments of the invention are characterized in what is set forth in the other claims.

An advantage of the apparatus according to the invention is its simple and inexpensive construction, which is lightweight and fits into a small space, and does not have a large number of moving parts. This ensures reliable operation of the equipment and does not require frequent maintenance or repairs. A further advantage is that, due to the balancing structure of the apparatus, remote control devices can, for example,

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. low-power power units, such as electric motors, to operate the equipment. This saves a great deal of energy.

Is compared to prior art equipment. The advantage

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£ is also that, in the apparatus of the invention, a rotatable body, such as a traffic boom or a car hood,

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10 etc. is in equilibrium in all positions and the downward direction is ...... .. ..

o The moving movement is against rising power. Then turn

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the piece is safe because it cannot fall unexpectedly downwards and does not cause the resulting hazards. It is also an advantage that the balancing apparatus according to the invention can be built at the factory as a component structure comprising only a balancing machine part. Thus, a small machine component is an easy-to-pack, lightweight and compact product that can be easily transported for sale anywhere in the world. On site, the equipment is merely mounted on its stand and a pivotable body, such as a traffic boom 10, which may have been purchased from a manufacturer other than the balancing equipment, is mounted on the pivot axis of the equipment.

The invention will now be described in more detail by way of example with reference to the accompanying simplified drawings, in which Figure 1 is a side and schematic view and a simplified view of one apparatus for turning a traffic boom and removing the front panel of the body; Figure 3 is a side elevational view, schematically, and simplified of the operation of the apparatus of Figure 1 with the boom turned 45 degrees.

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Fig. 1 is a side elevational view and diagrammatic view of one embodiment of an apparatus according to the invention for turning a part 1 such as a traffic boom.

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S with the center part of the front panel 2a cut off, σ> 30 and other front parts removed. Katsomasuunnassa

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io The boom 1 in front of the apparatus is shown as a point break ....

o with butter so that it does not cover behind the equipment. Similarly, Fig. 2 shows a top view, simplified and partially sectioned of the apparatus 4 according to the invention.

The apparatus shown in Figures 1 and 2 includes at least a housing-like body portion 2 having a front plate 2a and a back plate 2b, 5 which plates 2a and 2b are substantially similar to each other which serve as the apparatus body and the shaft bearing supports; fastened to each other, for example, by means of fastening means 13 so that there is a space between the plates 2a and 2b for the balancing mechanism 3. 10 The balancing mechanism comprises at least a transmission element 4 with a transmission shaft 5 with which the transmission element 4 pivots. The transmission shaft 5 is mounted on the body 2 by means of bearings 5a. Further, the balancing mechanism 3 includes a compensating member 9 for balancing the variable force caused by the weight of the movable body 1, such as a prestressed torsion spring, the first end 9a of which is fixedly adjustable to a flange 5b on the drive shaft 5. Thus, the flange 5b transmits the torsion to the spring force transmission shaft 5 of the spring 9. The other end 9b of the torsion spring 9 20 is secured to the front plate 2a of the body.

The balancing mechanism 3 further comprises a pivoting member 7 which is mounted on the pivot axis 8 and is adapted to pivot along with the pivot axis 8 and act as a transmission ratio modifier. The pivot shaft 8 is mounted on the body 2 by means of a bearing - <- 25 thighs 8a. The first end of the pivot axis 8 is

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, a fixed piece 1, for example a traffic boom, adapted to be balanced by a balancing mechanism 3. At the other end, the center of gravity of the attached boom 1 moves the boom

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£ when turning along a closed circular path and the torque caused by boom 1 burns 30o on the pivot axis 8 changes the boom

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o The biased torque changes linearly. Stabilization-

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the machine 3 is arranged to linearly adjust the torque 9 of the torsion spring 9 as a function of the cosine of the pivoting angle caused by the boom 1 so that the forces exerted on the belt 6 of said moments are equal to each other but opposite in all angular positions.

The balancing mechanism 3 further comprises a power element 12 at one end of the pivot shaft 8, attached to the rear plate 2b of the body part, such as an electric motor adapted to pivot the pivot shaft 8 when necessary, for example in automation control. Further, the balancing mechanism 3 includes a power transmission member 6, such as a belt fastened at its first end to the transmission member 4 by a fastening member 10 and a second end to a pivoting member 7 by a fastening member 11 and tightened to a suitable tension before attachment 15 by a tension adjusting member. The force member 12 is required to counteract the friction and possible external forces in all positions of the boom 1 and to keep the force selector member 6 always tight enough.

1 and 2, the boom 1 is in its horizontal position and the moment caused by the weight of the boom 1 is at its maximum. Similarly, the torque 9 of the prestressed torsion spring 9 on the transmission shaft 5 of the transmission member 4 is at its maximum, whereby the torsion spring 9 attempts to push the boom 1 upward with maxi-g 25 of its minimum force. Correspondingly, the weight of boom 1 tends to press

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i boom 1 size a] an down. With the boom 1 horizontal, the forces of the boom 1 and the torsion spring 9 are transmitted to the belt 6 via the contact points 14 and 15 and the boom being

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£ in the upright position, the forces are transmitted to the belt 6 via the contact points σ> 30 14n and 15n, which are not, however, tf), ...

shown in the figures.

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The transmission member 4, the pivoting member 7 and the torsion spring 9 are dimensioned, as the case may be, with respect to the boom 1 such that the forces on the strap 6 are equal with each other pivoting position of the boom 1 so that the boom 1 is balanced in all pivoting positions. Thus, the force acting on the belt 6 is equal at the contact point 5 14 ... 14n between the belt 6 and the pivoting member 7 and at the contact point 15 ... 15n between the belt 6 and the transmission member 4. The effective force at the point of contact 14..14n is determined by the moment caused by the pivotable boom 1 and the radius of the point of contact 14 ... 14n, i.e. the distance of the point of contact 14 ... 14n to the center line of the pivot axis 8. This distance 10 is later described by the turning radius R7. Correspondingly, the force acting on the contact point 15 ... 15n is determined by the torque 9 of the torsion spring acting on the transmission shaft 5 and the distance of the contact point 15 ... 15n to the center line of the transmission shaft 5. This distance is later described by the term 15 turning radius R5.

The torsion spring 9 acts as a renewable energy reservoir, releasing energy when raising boom 1 and collecting energy when lowering boom 1.

Figure 3 is a side elevational view and schematically illustrating the operation principle of one apparatus according to the invention. In the exemplary situation of Fig. 3, boom 1 is rotated at an angle of 45 ° from its upward or downward position. In this case, the pivoting member 7 attached to the pivot shaft 8 also pivots by 45 °, i.e. g 25 by an angle B, but the transmission member 4 is in shape and pivotable.

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As a result of the mutual dimensioning of the member 7 and the transmission member 4, the length of the contact surface 4a corresponding to the angle B,

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the retaining member 4 corresponds to the length of the belt 6 30 released from the pivoting member 7. In this example, the dimensioning of the transmission member 4, the pivoting member 7 ^ and the torsion spring 9 is such that, when the boom 10 ° is rotated 90 °, the transmission member 4 turns about 276 °.

The pivoting member 7 has a contact surface 7a of the belt 6 which is at least 90 ° the length of a circle S having a radius R7 of a circle corresponding to a circle sector. In practice, the contact surface 7a extends on either side of the arc S for some distance, but in this area outside the arc, the contact surface 7a need not necessarily have a circular arc. The angle C of the circular sector is 90 ° in this case, but it may also be 90 °, depending on the application. Seen from the side, the shape of the pivoting member 7 resembles a fourth to 10 sub-circular sectors of a circle having two substantially straight sides and an arcuate surface between them. Further, near the point of intersection of the straight sides, there is a hole for the pivot axis 8 such that the pivoting radius 15 R7 of the pivoting member 7 is substantially constant at least in the circle sector of the angle C. The turning radius R7 here refers to the length of the radius S of the arc S, i.e. the contact surface 7a, from the central axis of the pivot axis 8. The turning radius R7 may also be continuously variable instead of constant.

The contact surface 4a of the belt 6 of the transmission member 4 is defined so that the turning radius R4 of the transmission member 4 is continuously variable according to the turning angle of the transmission member 4. Hereby, the magnitude of the turning radius R4 at each pivot position of the drive member 4 is selected such that the belt 6 is subjected to substantially the same force as the torsion spring 9 at the point of contact 15a of the belt 6 and the contact surface 4a of the drive member 4a. 1 torque applied to belt 6, but in the opposite direction. Hereby, the instantaneous turning radius R4 x of the actuator 4 is dimensioned to correspond to the current torque of the torsion spring 9: 30 and such that the turning radius R4 is at maximum σι [jf when the moment produced by the weight of the boom 1 is maximal that is, the boom 1 is in horizontal position.

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As the boom 1 is turned upward, the torque caused by the boom 1 on the pivot axis 8 decreases as a function of the cosine of the pivot angle and the torque of the torsion spring 9 decreases as the spring preload decreases. At the same time, the pivoting radius R4 of the drive member 4 at the point of contact between the belt 6 and the contact surface 4a changes so that the force exerted by the spring 9 is equal to the force exerted by the moment 1 of the boom. When boom 1 is upright, both moments are substantially 10 zeros.

Whereas, as the boom 1 descends towards its horizontal position, the moment caused by the boom 1 on the pivot axis 8 increases as a function of the cosine of the pivot angle and the torsion spring 9 tightens. At the same time, the turning radius R4 of the drive member 4 at the point of contact of the belt 6 and the contact pin 15a 4a is changed such that the force exerted by the spring 9 is equal to the force exerted by the moment 1 of the boom. The turning radius R4 acting as a torque arm is the distance between the belt 6 and the contact point 15, 15a ... 15n 20 of the transmission member 4 and the central axis of the transmission shaft 5, which thus varies as a function of the turning angle of the transmission member 4. Since the pivot angle of the boom 1 via the belt 6 also affects the pivot angle of the gearing member 4, the pivoting angle of the gearing member 4, and thus also the pivoting radius R4, changes by a half-25 min 1 as a function of pivot angle.

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The prestress ya of the torsion spring 9 and the pivoting radius R7 T of the cap member and the pivoting radius R4 of the transmission member are dimensioned such that the belt 6 is affected by the contact between the belt and the transmission member 4.

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In the dies 14, 14a ... 14n and 15, 15a ... 15n, the force, ^ 30, which is applied by the rotational axis 8 through the pivot axis 8 to the transmission member 4, is constant by the force 3030.

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For example, when the boom 1 and at the same time the pivot axis 8 are pivoted upwards by 10 °, a certain amount of 9 belts 6 is released from the pivoting member 7 so that the gearing member 4 is pivoted so that exactly the same number of belts 6 are wrapped around the gearing member. Otherwise, the strap 6 will remain loose or break. Starting from the horizontal position of the boom 1, in this example, with the boom turning angle of 10 °, the pivoting angle 4 of the actuator 4 is about 24 °, but as the pivoting radius R4 of the pivoting member 4 is continuously decreasing, larger and larger turning angle. Finally, when the pivoting member 7 10 is rotated 90 °, the transmission member 4 is pivoted about 276 °.

It will be apparent to one skilled in the art that the various embodiments of the invention are not limited to the examples above, but may vary within the scope of the following claims. Thus, for example, instead of a belt acting as a power transmission means, the transmission means may also be a steel rope, chain or other similar and suitable force transmission means.

It will also be appreciated that the shape and contact surface of the actuator may be such that, instead of an angle of 276 °, the actuator 20 will, for example, only rotate 180 ° when the boom or other vertically pivotable body rotates 90 °. However, a stiffer torsion spring is required.

It is also clear that the shape and contact surface of the gear member may be such that the gear member rotates several turns, i.e., over 360 °, when the boom or other vertical plane

The rotating workpiece rotates 90 °.

h- x It is also clear that the spring structure can also be made with cc nested springs, which allows for a highly competitive solution.

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In addition, it is further understood that the torsion spring structure shown in the example, acting as a compensating member, may be replaced by another force member capable of providing a counter-force against the weight of the boom.

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Apparatus for substantially balancing a reciprocating body (1) in a substantially vertical plane along a circular or other closed path, comprising at least a frame member (2) and a pivot axis (8) hinged to the frame member (2) on which the movable body (1) ) is mounted and has at least a compensating member (9) for balancing the variable force caused by the weight of the movable body (1) and means for transmitting the 10 moments of the compensating member (1) to the pivot axis (8) of the movable body (1) rod (6) and a gear member (4) attached to the transmission shaft (5), characterized in that the pivoting angle of the gear member (4) on the gear shaft (5) is different from that of the gear (15) and the gear member (4). the turning radius (R4), i.e. the distance between the contact point (15, 15a ... 15n) between the transmission means (6) and the transmission means (4) and the central axis of the transmission shaft (5) is variable as a function of the angle of rotation of the transmission shaft (5).

Apparatus according to claim 1, characterized in that the pivot shaft (8) and the transmission shaft (5) are interconnected by means of a power transmission means (6), and a transmission means (4) attached to the transmission shaft (5) is arranged by means of power transmission means 1) with a pivotal movement of 25 substantially greater than the angle of inclination

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1 le (1), and at the same time the rotational radius (R4) of the conveying member (4), which is continuously changing with the pivoting angle 4, is adapted to change as a function of the pivot angle of the body (1).

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Apparatus according to claim 1 or 2, characterized in that the power control wall (6) of the transmission member (4) is σ>. . ..

o the contact surface (4a) facing is defined such that

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the pivoting radius (R4) of the transmission means (4) is continuously variable, and the pivoting radius (R4) of the transmission means (4) is adapted to change by the transmission means (6) attached to the transmission means (4) as the pivoting angle of the force exerted by the torque transmission member (4) and the force exerted by the compensation member (9) on the transmission member (4) 5 are equal and opposite in direction, and the rotational angle of the piece (1) decreasing such that 9) the force exerted by the torque on the transmission member (4) is equal in magnitude and opposite in direction.

Apparatus according to claim 1, 2 or 3, characterized in that the variable length of the pivoting radius (R4) of the actuator (4) at different angles of pivot (4) is selected such that the forces exerted by the position of the body (1) (6) are substantially equal to each other in the pivoting angle of the body (1), wherein the body (1) is substantially balanced at all its pivot angles.

Apparatus according to one of the preceding claims, characterized in that a pivoting member (7) acting as a gear ratio changer is mounted on the pivot axis (8), whose pivoting radius (R7) is greater than the respective pivoting radius (R4) of the pivoting member (4).

A device according to any one of the preceding claims, characterized in that the pivoting radius A (R7) of the pivoting member (7) is substantially constant throughout the pivoting angle of the body (1).

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Illegal body according to one of the preceding claims, characterized in that the power transmission element (6) is already a strap, a steel rope or a chain fastened at its first end to the transmission element (4) and at its second end to the pivoting element (7).

Apparatus according to one of the preceding claims, characterized in that the compensating member (9) is a torsion spring, the first end (9a) of which is fixedly adjustable by a flange (5b) to the transmission shaft 5 (5) and the other end of which part (2) and is adapted to provide an upwardly turning force of the piece (1) and to store the energy generated when the piece (1) is turned down.

Apparatus according to one of the preceding claims, characterized in that the apparatus comprises a power element (12) arranged to pivot the cover shaft (8), such as an electric motor.

Apparatus according to one of the preceding claims, characterized in that the body (1) movable in a substantially vertical plane is a traffic boom, skylight, hatch, tilt door, car bonnet, tailgate or lever and associated masses or a lifting bridge, or the like, which is pivotable from one edge of the joint to a substantially vertical direction 20.

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Claims (10)

A device for balancing a body (1) moving forward and eating along a circular or other closed path substantially in the vertical plane, said device comprising at least one body member (2) and one guided in the body member (2) rotary shaft (8) into which the movable body (1) is attached and which device is provided with at least one compensating member (9) which balances the changing force caused by the weight of the movable body (1), and equipment, such as a switching shaft (5), a power switching means (6) and a switching means (4) fixed to the switching shaft (5), which transfers the torque generated by the compensating member (9) to the rotating shaft (8) of the movable body (1) , characterized in that the angle of rotation of the switching means (4) located on the switching shaft (5) and the corresponding turning angle of the body (1) are different and the turning radius (R4), ie. the distance between the mutual contact point (15, 15a ... 15n) of the power switching means (6) and the switching means (4) of the switching shaft (5) changes as a function of the turning angle of the switching shaft (5). Device according to claim 1, characterized in that the rotary shaft (8) and the switching shaft (5) are connected to each other via the power switching means (6), and the switching means (4) fixed to the switching shaft (5) is arranged that by means of the power mediator (6), together with the rotational movement of the body (1), an angle which is substantially CVI, 1 gene is greater than the rotational angle of the body (1), and at the same time the median of the mediator (4) is continuous varying radius of rotation (R4) arranged to change X ϊ as a function of the turning angle of the body (1). CJ) two Device according to Claim 1 or 2, characterized in, CD § 35, that the contact surface (4a) of the switching means (4) against the power switching means (6) is designed so that the turning radius (R4) of the switching means (4) is changed continuously, and the switching means (4) ) rotary radius (R4) under the influence of the power switching means (6) attached to the switching means (4) is arranged that as the turning angle of the body (1) increases, so that the momentum caused by the body (1) on the switching means ( 4) the actuating force and the momentum caused by the compensating member (9), the force acting on the mediating member (4) is equal to Large but opposite in direction and when the angle of rotation of the body (1) decreases so that it caused by the moment of the body (1); the force acting on the mediating means (4) and the force caused by the compensating means (9) acting on the mediating means (4) are equally Large but opposite in direction. Device according to claim 1, 2 or 3, characterized in that the variable length of the rotating radius (R4) of the switching means (4) at different pivoting angles of the switching means (4) is selected so that they are positioned and compressed by the body (1). the tensioning means (9) generated by the force mediating means (6) acting at all the angles of rotation of the body (1) are substantially equal between each other, the body (1) being substantially equal in all its angles of rotation. Device according to any of the preceding claims, characterized in that a rotating member (7) which changes the gear ratio is attached to the rotating shaft (8), the rotating radius (R7) of the rotary member (7) being larger than the switching member (4). ) instantaneous rotational radius (R4) at each time. o CM d- Device according to any of the preceding claims, characterized in that the rotating radius (R7) of the rotary member (7) is substantially constant in the entire rotational angle range of the body (1). X X CL σ> 7. Device according to any of the preceding claims, characterized in that the power conveying means (6) is, for example, a belt, a scaffold or a chain, which in its first CM is only fixed in the intermediary means (4) and at its other end in the swivel (7). Device according to any of the preceding claims, characterized in that the compensating means (9) is a torsion spring whose first end (9a) to the position is adjustably attached to the intermediate shaft (5) via a flange (5b) and the other end thereof. is attached to the front plate (2a) of the body part (2) and which is arranged to generate the force which rotates the body (1) upwards and stores the energy which increases when the body (1) is rotated downwards. 10 Device according to any of the preceding claims, characterized in that the device comprises a power means (12) arranged to rotate the pivot shaft (8), such as an electric motor. 15 Device according to any of the preceding claims, characterized in that the body (1) which moves substantially in the vertical plane along a circular path is a traffic boom, a skylight, a hatch, a tilting gate, a car's hood, a luggage cover. or even a lifting bridge or some equivalent, around a joint at one edge substantially in the vertical plane rotatable construction. δ Ovi h- X X CL σ> LO LO CD O o OJ