Articulated joint for deploying and locking a solar generator or a reflector

Abstract

A joint for unfolding and locking a solar generator or a reflector, or other aerospace components that can be unfolded, includes two half joints, a joint axis, and a drive. A drive spring of the drive has a progressive characteristic curve over the unfolding angle of the two half joints, which increases over the unfolding, to compensate for a frictional torque that varies over the unfolding angle.

Claims

1. A joint for unfolding and locking a solar generator, a reflector, or other aerospace components that can be unfolded, consisting of: two half joints; a joint axis; and a drive, wherein a drive spring of the drive has a spring characteristic curve that compensates for a frictional torque that varies over the unfolding angle, the characteristic curve increasing over the unfolding progressively, over the unfolding angle of the two half joints.

2. The joint of claim 1, wherein the spring characteristic curve corresponds, over the entire unfolding angle, to at least a predetermined multiple of the frictional torque.

3. The joint of claim 2, wherein the predetermined multiple of the frictional torque is triple of the frictional torque of the half joints rotated against each other.

4. The joint of claim 2, wherein the spring characteristic curve corresponds, over the entire unfolding angle, exactly to the predetermined multiple of the frictional torque.

5. The joint of claim 4, wherein the predetermined multiple of the frictional torque is triple of the frictional torque of the half joints rotated against each other.

6. The joint of claim 1, wherein the drive is a constant force spring B-motor, wherein the drive spring is arranged on a drive roll, and a fixed end of the drive spring is fixed to the drive roll, and a free end of the drive spring runs around the joint axis.

7. The joint of claim 6, wherein the drive spring has a non-rectangular shape when it is extended.

8. The joint of claim 7, wherein the drive spring has a trapezoidal shape that is narrower towards its free end.

9. The joint of claim 6, wherein a natural radius of the drive spring is greater towards its free end.

10. The joint of claim 6, wherein the drive spring is formed from multiple leaves of different lengths.

11. The joint of claim 6, wherein the drive spring has one or more recesses along its center line.

Description

BRIEF DESCRIPTION OF THE DRAWING FIGURES

(1) The invention is described in greater detail below with reference to an embodiment in the drawings, wherein:

(2) FIG. 1 shows a side view of a joint for unfolding and locking a solar generator or reflector, the principle of which is known,

(3) FIG. 2 shows a top view of the joint in FIG. 1,

(4) FIG. 3 shows a cutaway view along line A-A of the joint in FIG. 2,

(5) FIG. 4 shows a view of the joint in FIG. 1, in direction B,

(6) FIG. 5 shows a perspective view of the joint in FIG. 1,

(7) FIG. 6 shows a first embodiment of an extended drive spring for use in a joint according to FIGS. 1 to 5,

(8) FIG. 7 shows a second embodiment of an extended drive spring for use in a joint according to FIGS. 1 to 5, and

(9) FIG. 8 shows a third embodiment of an extended drive spring for use in a joint according to FIGS. 1 to 5.

DETAILED DESCRIPTION

(10) A joint according to FIGS. 1 to 5, for the purpose of unfolding and locking solar panels of a solar generator, which are not illustrated here, has a fixed half joint 4 and a half joint 10 that is able to pivot, the same having a common axis 8 (cf. FIGS. 1 and 3). The fixed half joint 4 is termed a bearing support, and the pivotable half joint is termed a fork. The pivotable half joint 10 is mounted on the axis 8 in a manner allowing rotation. In FIG. 1 to FIG. 5, it is pivoted fully out by means of a drive spring 1 arranged on the axis 8. This means that solar panels (which are not illustrated), which are attached to the two half joints 4, 10 via round billets, lie in a plane, and/or are pivoted with respect to each other at an angle of 180°.

(11) A fixed end of the drive spring 1 arranged on a drive roll, wherein the same is not visible in detail, is bolted to the fixed half joint 4 by means of connecting elements 11, 12, 13 (cf. FIG. 1 and FIG. 3). In addition, a locking fork 16 is mounted on the pivotable half joint 10, and receives a locking bolt 5. A yoke spring 6 is attached on the pivotable half joint 10, and shares an axis with the locking fork 16, wherein the legs of said yoke spring 6 pass through a head of the locking bolt 5 (cf. FIG. 1 and FIG. 2). The locking fork 16 and the yoke spring 6 are attached together to the pivotable half joint 10 by means of a screw 45. In FIGS. 1 to 5, the locking bolt 5 is pressed by the yoke spring 6 into a groove (FIG. 2), thereby locking the pivotable half joint 10 to the fixed half joint 4.

(12) The principle of the construction of this joint is known, by way of example, from German patent document DE 196 49 741 A1, such that no further discussion is provided on the further details of the joint which are illustrated but which are not requisite for understanding the invention.

(13) The drive spring 1 is, as can best be seen in FIG. 2, designed similarly to a constant force spring B-motor. The drive spring 1 is arranged on a drive roll, wherein a fixed end of the drive spring 1 is fixed to the drive roll, and a free end of the drive spring 1 runs around the joint axis 8. A drive spring designed in such a manner is fundamentally capable of releasing a constant unfolding torque over the actuation of the drive spring—meaning over the unfolding angle from 0° to 180°.

(14) In order to keep the load on the materials of the individual components of an unfolding mechanism low—for example synchronization cables, rods, pulleys 9, and brackets, unfolding speed regulating mechanisms (motor gear unit MGU), etc.—a drive spring 1 used in the joint illustrated in FIGS. 1 to 5 has a progressive spring characteristic curve, which increases over the unfolding. In this way it is possible to compensate for a frictional torque that varies over the unfolding angle. Such a frictional torque that varies over the unfolding angle, and particularly increases, is primarily caused by the electrical conductors (not illustrated) of the solar generator or reflector, the same being routed across the joint axes and deformed during that unfolding.

(15) The progressive spring characteristic curve functions such that the drive spring releases a lower torque at the beginning of the unfolding (starting from an angle of 0°) than at the end of the unfolding. The spring characteristic curve, which is determined by a geometrical design of the drive spring, is sized in this case in such a manner that it has a spring characteristic curve over the entire unfolding angle of 0 to 180° which preferably at least corresponds to the triple of the frictional torque. In this way, even in the worst case (with high frictional torques caused by the electrical conductors used for the purpose of transmitting electrical power), it is possible to provide an opening torque that is higher than the sum of all the applied frictional torques.

(16) Such a characteristic curve of the drive spring 1 can be achieved in various different ways. By way of example, as is illustrated in FIGS. 6 and 7, the drive spring can be designed to be narrow towards its free end. When the solar generator is folded closed, the free end of the drive spring 1 is active. When unfolding, the active region of the drive spring shifts toward its inner, fixed end. Therefore, if the spring is wider towards the fixed end, the spring torque constantly increases over the unfolding.

(17) In the embodiment variant according to FIG. 6, the spring 1 has a width b on its fixed end, the same being arranged on the drive roll. The width b is maintained over a length l.sub.1. Subsequently, the spring becomes narrower towards its free end over the length l.sub.0, to a width b.sub.0 which is smaller than the width b. The entire length l of the spring, illustrated as extended, is therefore l=l.sub.1+l.sub.0.

(18) In contrast, the embodiment variant according to FIG. 7 shows a trapezoidal shape which has a lesser width b.sub.0 towards its free end than on its fixed end. Moreover, the spring which is illustrated in the embodiment in FIG. 7 as extended has an optional recess on the center line of the spring. In this case, only one single recess 50 is illustrated.

(19) In a modification, which is not illustrated, multiple recesses arranged one behind the other could also be included on the center line of the spring, having the same or different lengths. The width of the recess is based on the spring characteristic curve to be achieved. The recess(es) could likewise be included in the embodiments according to FIGS. 6 and 8.

(20) In a further modification, the outer contour of the extended spring can also have any other shape, if the same is suitable for providing the desired spring characteristic curve.

(21) FIG. 8 shows a further embodiment of a drive spring 1 in a side view, wherein the drive spring 1 consists, as an example, only of a total of six individual leaves 1a, 1b, 1c, 1d, 1e, 1f. The leaves have different lengths. At the start of the unfolding, only a few spring leaves are active, on the free end of the drive spring. The more the joint opens, the more spring leaves are applied which in turn leads to the desired, increasing spring torque. The spring characteristic curve is not constant, in contrast to the variants illustrated in FIGS. 6 and 7. Rather, it has a nearly step-like profile.

(22) In a further embodiment which is not illustrated, the natural radius of the drive spring is greater towards its free end. This can be achieved, by way of example, by a drive roll which is not circular. The radius of the drive roll in this case in incorporated into the formula for the calculation of the spring torque.

(23) The design variants shown in FIGS. 6, 7, and 8, as well as the last variant above, can be fundamentally combined with each other.

(24) In the sketched illustrations, the drive springs are illustrated in extended form, to clarify understanding of their design.

(25) By using a progressive drive spring, as shown in FIGS. 6 to 8, it is possible for a torque to be released at the start of the unfolding, as is generated in the constant force springs used to date. The unfolding mechanisms are not subjected to higher loads with respect to their strength than in a conventional joint. However, as a result of the spring torque that increases over the unfolding, a higher spring torque is obtained at the end of the unfolding—by way of example, a spring torque which is twice as large—such that it is even possible to work with greater frictional torques. The dimensioning is such that the spring torque of the spring characteristic curve is such that the same is greater than the sum of all applied frictional torques by a factor of 3, at least at the end of the unfolding.

(26) The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.

LIST OF REFERENCE NUMBERS

(27) 1 drive spring 4 (fixed) half joint 5 (locking) bolt 6 yoke spring 8 axis of rotation 9 pulley 10 (pivotable) half joint 11 connecting element 12 connecting element 13 connecting element 16 locking fork 45 screw 50 recess