CN209856738U - Vertical positioning equipment, vertical damping device and have its stabilizer and shooting equipment - Google Patents

Abstract

The utility model provides a vertical damping device that is used for the shock attenuation to come from the vertical vibrations of supporting structure, it includes: a counterbalance mechanism pivotally mounted on the support structure about a pivot axis; a rotation-linear motion converting mechanism that vertically supports the load; a force generating mechanism; and when the balance mechanism rotates in any direction, the load is driven to move in the opposite direction of the vibration direction through the rotation-linear motion conversion mechanism under the condition of keeping the balance of the gravity of the load. From this, provide a vertical damping device that reaction is sensitive, simple structure, compensation effect are good. Further, a vertical positioning device of the load, a stabilizer for an imaging device, and a photographing device are also provided.

Description

Vertical positioning equipment, vertical damping device and have its stabilizer and shooting equipment

Technical Field

The utility model relates to a vibrations suppression and position control technical field, concretely relates to vertical positioning device, vertical damping device and have such vertical damping device's stabilizer and shooting equipment.

Background

For high precision electromechanical systems, such as measuring machines, manufacturing machines, optical instruments or photographing devices, it is important to avoid or minimize vibrations or jitter from the external environment as much as possible to maintain the desired position of the functional components in the system.

For example, in the case of a stabilizer, when a user directly holds the stabilizer to photograph, the user is likely to shake the stabilizer vertically, which affects the photographing effect and reduces the definition of a picture. To unmanned aerial vehicle or unmanned vehicle carried image device, because the influence of jolting or the air current on road surface also can produce unexpected vertical vibrations to be unfavorable for the promotion of shooting the effect.

It is known to damp loads mechanically by means of elastic or damping elements, which however, in practice, have been found to often only act to cushion and store the impact force, delaying the release, but do not hold the functional component (e.g. the lens) in the desired position in the vertical direction as described above, and are therefore not satisfactory. On the basis of this, it has been proposed to vertically compensate for the displacement of the functional component from the desired position in case of a shock by means of an actuator device such as an electric motor, but since the functional components are often very heavy, the electric motor is required to have a very large torque, which means that the electric motor is bulky, energy consuming and requires a very good heat dissipation, which is not at all practical for self-contained power products such as stabilizers or drones or unmanned vehicles where miniaturization and light weight are important.

Accordingly, there remains a need in the industry to provide a satisfactory, commercially viable vertical shock absorbing device and vertical positioning apparatus.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a vertical damping device that can solve above-mentioned prior art's all sorts of deficiencies at least partially.

According to an aspect of the present invention, there is provided a vertical shock absorbing device for absorbing vertical shock from a support structure, for supporting a load, wherein the vertical shock absorbing device comprises: a balancing device, comprising: a rotation shaft having a pivot axis and mounted on the support structure and a balancing mechanism rotatable about the rotation shaft; a rotation-to-linear motion conversion mechanism vertically supporting the load, configured to be operatively connected to the counterbalance mechanism at a first distance from the pivot axis on one side thereof to apply a first torque to the counterbalance mechanism in a first rotational direction under the weight of the load; a force generating mechanism configured to be operatively connected to the balance mechanism at a second distance from the pivot axis on the other side of the balance mechanism to apply a second torque to the balance mechanism in a second rotational direction opposite the first rotational direction under the force applied by the force generating mechanism, the force generating mechanism being fixedly connected at one end to the support structure; when the balance mechanism is subjected to vertical vibration and is in different angular positions, the load is driven to move along the direction opposite to the vibration direction through the rotation-linear motion conversion mechanism under the condition of keeping the gravity for balancing the load when the balance mechanism rotates along any direction.

From this, compare with prior art, via providing according to the utility model discloses a vertical damping device has changed mechanical shock attenuation's design from the radical function principle, wherein sets up load with weightless mode suspension to thereby realized initiatively compensating vertical upward displacement when accepting the vertical vibrations that come from external environment and obtained a vertical damping device sensitive, simple structure, that the compensation is effectual with reliable and low-cost mode via mechanical design.

In a preferred embodiment, wherein the balance mechanism includes a circular gear and a pulley at least partially having a variable radius with angle, which are coaxially arranged, wherein the rotation-linear motion conversion mechanism is configured to include a rack gear engaged with the circular gear. Thus, by such a design, damping of vertical vibrations is achieved in a reliable and highly accurate manner of vertical displacement compensation.

In a preferred embodiment, wherein the balancing mechanism comprises: the rotation-linear motion conversion mechanism comprises a sliding part fixedly arranged at the outer end of the swinging part, and a linear displacement part with a sliding chute in sliding connection with the sliding part, so that the rotation swing of the swinging part is converted into the linear motion of the linear displacement part. Thereby, friction losses present in the vertical damping device are further reduced, which may improve the sensitivity of the vertical damping device to reactions to external vertical shocks and the accuracy of the compensation.

In a preferred embodiment, the force generating mechanism comprises: the spiral spring can be wound or unwound along the spiral direction; a guide wheel disposed coaxially with the spiral spring;

and a linear member connecting the guide wheel to the balance mechanism, wherein one end of the spiral spring is fixedly connected to the guide wheel and operatively connected to the balance mechanism via the linear member, and the other end of the spiral spring is fixedly connected to the support structure so that the spiral spring can be wound or unwound as the balance mechanism rotates, wherein the linear member is guided along an outer periphery of the balance mechanism. Thereby, the force generating mechanism is arranged in a compact manner, allowing miniaturization of the vertical damping device.

In a preferred embodiment, the adjusting mechanism is used for adjusting the pretightening force of the volute spring, and comprises: the rotating shaft is fixedly connected with the other end of the spiral spring; and a worm wheel rotatably positioned on the support structure and connected to the shaft, and a worm cooperating with the worm wheel, wherein the worm wheel and the shaft connected thereto are driven by rotating the worm to adjust the preload of the volute spring. Therefore, the vertical damping device can adapt to loads with different weights, and the universality of the vertical damping device is improved.

In a preferred embodiment, the adjusting mechanism is used for adjusting the pretightening force of the volute spring, and comprises: the ratchet wheel is fixedly connected with the other end of the spiral spring; and a pivotable pawl fixedly mounted to the support structure and engaged with or disengaged from the ratchet wheel, wherein the pivotable pawl when engaged to the ratchet wheel locks the volute spring in an angular position having a predetermined preload force. This allows the vertical damping device to be adapted to loads of different weights in a simple manner, thereby increasing the versatility of the vertical damping device.

In a preferred embodiment, the force generating mechanism comprises: any one of a coil spring capable of being stretched or retracted in a linear direction, a hydraulic damper capable of being stretched or retracted in a linear direction, or a combination thereof, wherein one end of the force generating mechanism is fixedly connected to a linear member and is operatively connected to the balance mechanism via the linear member and the other end is fixedly connected to the support structure so that the force generating mechanism can be stretched or retracted with rotation of the balance mechanism, wherein the linear member is guided along an outer periphery of the balance mechanism. Thereby allowing the vertical damping device to be manufactured and produced in a cost-effective manner.

In a preferred embodiment, a guide wheel for deflecting the wire is further included. Thereby, the wire-shaped member can be allowed to reliably maintain contact with the balance mechanism throughout the operation of the vertical shock absorbing device.

In a preferred embodiment, a mechanism for adjusting the pre-load force of the coil spring is further included, which includes: an adjusting screw which is screwed to the support structure and is fixedly connected to the other end of the helical spring, wherein the pretension of the helical spring is adjusted by screwing the adjusting screw in or out relative to the support structure. This allows the vertical damping device to be adapted to loads of different weights in a simple manner, thereby increasing the versatility of the vertical damping device.

In a preferred embodiment, the apparatus further comprises a guide mechanism provided in parallel to the moving direction of the rotation-linear motion converting mechanism, wherein the guide mechanism comprises: the linear guide device comprises at least one guide rail arranged in parallel to the motion direction of the rotation-linear motion conversion mechanism, at least one linear bearing arranged on the guide rail in a penetrating mode, and a support capable of sliding guided along the guide rail through the linear bearing, wherein the support is fixedly connected with the rotation-linear motion conversion mechanism to achieve linear guide of the rotation-linear motion conversion mechanism. Hereby, a vertical guidance of the rotation-to-linear motion converting mechanism and the load connected thereto is achieved in a cost-effective and reliable manner.

According to another aspect of the present invention, there is also provided a vertical positioning apparatus for a load, comprising a position sensor for measuring a position of the load, a position controller and a motor, wherein the position controller receives a signal of the position of the load from the position sensor and generates an output signal for controlling an action of the motor, wherein the positioning apparatus further comprises a vertical damping device for vertically supporting the load, wherein the motor is connected to the balancing mechanism to move the load in a direction opposite to a vibration direction via the action of the motor, thereby positioning the load at a determined position in a vertical direction. Hereby it is achieved that a certain position is ensured that the load is always located in the vertical direction.

According to another aspect of the present invention, there is provided a stabilizer for an image forming apparatus, including a supporting structure and a vertical damping device connected to the supporting structure for vertically supporting the image forming apparatus, wherein the vertical damping device includes: a balancing device, comprising: a rotation shaft having a pivot axis and mounted on the support structure and a balancing mechanism rotatable about the rotation shaft; a rotation-to-linear motion converting mechanism vertically supporting the image forming apparatus, configured to be operatively connected to the balance mechanism at a first distance from the pivot axis at one side of the balance mechanism to apply a first torque to the balance mechanism in a first rotational direction under the influence of gravity of the image forming apparatus; a force generating mechanism configured to be operatively connected to the balance mechanism at a second distance from the pivot axis on the other side of the balance mechanism to apply a second torque to the balance mechanism in a second rotational direction opposite the first rotational direction under the force applied by the force generating mechanism, and the force generating mechanism is fixedly connected at one end to the support structure; wherein when the balance mechanism is subjected to vertical vibration from the support structure to be in different angular positions, the image forming apparatus is driven to move in the opposite direction to the vibration direction via the rotation-linear motion conversion mechanism while keeping the balance of the gravity of the image forming apparatus when the balance mechanism is rotated in any direction. Thereby, the influence of vertical vibration on the image forming apparatus can be eliminated.

In a preferred embodiment, the balance mechanism further comprises a position sensor for measuring the position of the imaging device, a controller for receiving a signal of the position of the imaging device from the position sensor, and a motor connected with the balance mechanism, wherein the controller is used for controlling the motor to act to drive the balance mechanism to rotate according to the position information of the imaging device detected by the position sensor. Thereby, it is possible to quickly react to an external vertical shock and position the load at a determined position in the vertical direction.

According to the utility model discloses an on the other hand still provides a shooting equipment, and it includes imaging device, is used for alleviateing this imaging device's axial vibration's axial and increases steady device and be used for alleviateing this imaging device's vertical damping device.

Additional features and advantages of the invention will be set forth in part in the description which follows, and in part will be apparent to those having ordinary skill in the art upon examination of the following, or may be learned from the practice of the invention.

Drawings

Embodiments of the present invention are described in detail below with reference to the attached drawing figures, wherein:

figure 1 shows a front view of a vertical shock absorbing device according to the present invention with parts removed to better show the internal structure of the device;

fig. 2 shows a front view of the vertical damping device according to fig. 1;

figure 3 shows a front view of another vertical shock absorbing device according to the present invention;

FIG. 4 shows a bottom view of the vertical damping device according to FIG. 3;

fig. 5 shows a front view of another force generating mechanism according to the present invention;

6-7 illustrate front views of adjustment mechanisms for adjusting the pretensioning force of the force-generating mechanism according to the present invention;

fig. 8 shows a front view of a stabilizer for an image forming apparatus with a shock absorbing device according to the present invention.

Description of the reference numerals

1. Vertical damping device 2, pivotal axis A, pivotal axis 3 rotating wheel set

31. Gear member 32, pulley member 33, balance 331, sliding portion 34, outer periphery

4. Rotation-linear motion converting mechanism 41, rack 42, linear displacement member 421, slide groove

5. 5A. force generating mechanism 6, 6A. wire 61, 61A. guide wheel

7. Guide mechanism 71, guide rail 72, linear bearing 73, support 8 and motor

91. Sleeve 92, end cap 93, shaft 94, worm wheel 95, ratchet

96. Pawl 97, pivot 98, spring 10 support structure

Detailed Description

Referring now to the drawings, illustrative aspects of the disclosed vertical damping device will be described in detail. Although the drawings are provided to present some embodiments of the invention, the drawings are not necessarily to scale of particular embodiments, and certain features may be exaggerated, removed, or partially sectioned to better illustrate and explain the disclosure of the present invention. The position of some components in the drawings can be adjusted according to actual requirements on the premise of not influencing the technical effect. The appearances of the phrase "in the drawings" or similar language in the specification are not necessarily referring to all drawings or examples.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When a component is referred to as being "connected" to another component, it can be directly connected to the other component or intervening components may also be present. When an element is referred to as being "supported" or "disposed" on another element, it can be directly supported or disposed on the other element or intervening elements may also be present. Certain directional terms used hereinafter to describe the drawings, such as "transverse," "vertical," "front," "rear," "inner," "outer," "above," "below," and other directional terms, will be understood to have their normal meaning and refer to those directions as normally contemplated by the drawings. Unless otherwise indicated, the directional terms described herein are generally in accordance with conventional directions as understood by those skilled in the art. The terms "first," "second," and the like, as used herein do not denote any order, quantity, or importance, but rather are used to distinguish one element from another.

Some embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The embodiments described below and the features of the embodiments can be combined with each other without conflict.

In fig. 1, a vertical shock absorbing device 1 for absorbing vertical shock from a supporting structure according to an embodiment of the present invention is schematically shown, wherein the vertical shock absorbing device 1 is used for supporting a load. Here, the load may be an imaging device for capturing images and videos, for example, a digital camera or a video camera, or a mobile communication device such as a mobile phone or a tablet computer having an imaging function, and may also be a stabilizer on which the imaging device is mounted. Wherein the vertical damping device 1 comprises a balancing mechanism which is pivotally mounted on a supporting structure (not shown) about a pivot axis a, which balancing mechanism comprises, in the embodiment shown in fig. 1, as shown in fig. 1: such as a pivot shaft 2 pivotally supported via a pair of bearings on a support structure (not shown), wherein the axis of the pivot shaft 2 itself is designated as pivot axis a, a rotating wheel set 3 rotatable about the pivot axis a, at least in part, having a variable radius with angle. In the present embodiment, the rotating wheel set 3 comprises a circular gear 31 and a pulley 32 at least partially having a variable radius with angle, preferably the radius of the pulley 32 varies in an involute manner; the circular gear 31 and the pulley 32 may here be separately manufactured and then coaxially fixedly arranged on the pivot shaft 2 in a rotationally fixed manner relative to each other, for example fixedly connected to each other or glued, so that both the circular gear 31 and the pulley member 32 are allowed to always remain co-rotating. It is of course also conceivable to form the gear 31 and the pulley 32 in one piece. Likewise, it will be appreciated by those skilled in the art that the pivot shaft 2 may also be fixedly supported in the support structure, with the gear 31 and the pulley 32 fixedly connected to or integrally formed with each other being rotatable about the axis of the pivot shaft 2, e.g. via a bearing

A plurality of teeth are evenly distributed on the outer circumference of the circular gear 31, and a rotation-linear motion converting mechanism 4 for vertically supporting the load is provided in a substantially vertical tangential direction at the outer circumference of one side of the circular gear 31. As shown in fig. 1, the rotation-linear motion converting mechanism 4 herein is configured to include a rack 41 that meshes with the teeth of the gear member. An externally threaded portion for connection with a load (not shown) directly above the rack 41 is provided at an upper end of the rack 41, thereby fixedly connecting the rack 41 to the load. When a load is loaded above the rack 41, due to the weight of the load, a torque, which may be referred to as a first torque, can be applied to the circular gear 31 in the counterclockwise direction in the drawing with respect to the pivot axis 2 via the engagement of the rack with the teeth of the circular gear 31, wherein the arm of the torque is equal to the distance between the engagement point of the rack 41 and the circular gear 31 (i.e., the operative connection between the rotation-linear motion conversion mechanism and the balance mechanism) and the pivot axis a, and the distance is maintained when the circular gear 31 rotates in any direction because the radius of the circular gear 31 is constant. In this embodiment, the above-described torque is equal to the product of the weight force of the load and the distance between the rotation-linear motion converting mechanism 4 and the pivot axis a of the pivot shaft 2 (i.e., the radius of the circular gear 31).

Below the pulley 32, opposite the toothed rack 41 about the pivot axis a, a force generating mechanism 5 is provided, which here is a helical spring 5 that can be extended or retracted in the vertical direction. Wherein the lower end of the helical spring 5 is fixedly connected to the supporting structure (not shown), for example, the helical spring may be fixedly connected to the supporting structure in a pretension-adjustable manner. While the upper end of the helical spring 5 is operatively connected to a pulley 32 in the rotating wheel set 3 via a wire element 6, where the wire element 6 is for example a steel or nylon or carbon fiber wire, as long as it has a sufficient tensile strength. Without being limited thereto, the term "thread" is used herein to denote various connecting elements which may be flexible under suitable conditions (transmitting only tensile forces) or may be partially inflexible under suitable conditions (transmitting tensile or compressive forces). Further, in order to facilitate guiding and deflecting the wire 6, a guide wheel 61 is further provided near the pulley member 32, and the guide wheel 61 may be, for example, an idler wheel having a smooth outer peripheral surface.

As shown in fig. 1, the illustrated pulley 32 may be the flat pulley-like member. The pulley 32 includes a periphery 34 having a radius (referenced to the pivot axis a) that varies (e.g., in an involute fashion) along the periphery 34. As an example, the radius decreases at a predetermined rate when viewed in a clockwise direction in fig. 1. Further, the pulley 32 has a groove provided along its periphery 34 for receiving the wire-shaped member 6 so that the wire-shaped member 6 is guided along the outer periphery 34 of the pulley 32 having a variable radius with angle. As shown in fig. 1, the end of the wire 6 is fixedly mounted to ensure that the portion of the wire 6 contacting the pulley 32 is within the groove of the periphery 32 and does not move relative to the groove. As an example, the wire member 6 may be fixed by clamping or bonding in the side of the circular gear 31 or the pulley 32 other than the outer periphery. As a further improvement, the engagement of the wire 6 with the groove can also be designed such that sufficient friction is generated to avoid any undesired relative sliding of the wire 6 with respect to the groove. Preferably, in order to reduce the inertia of the balancing mechanism itself as much as possible to allow a response to a slight shock of the supporting structure, it is desirable to further reduce the mass of the balancing mechanism, and for example, it may be considered to hollow out a portion of the circular gear 31 or to make the pulley 32 of a light material.

When the pulley 32 rotates in any direction, the wire 6 is always in a state of force balance, i.e., the frictional force given to the wire 6 by the outer periphery 34 of the pulley 32 is equal to the tension in the wire 6 (also equal to the elastic force of the coil spring 5). The wire 6 will thus likewise give the pulley 32 a tangentially equally large force, under which a torque, which can be referred to as a second torque, will be exerted on the pulley 32 in the clockwise direction in fig. 1 relative to the pivot axis a. Wherein the torque is equal to the product of the elastic force in the force generating mechanism and the distance from the contact point (i.e., operative connection position) of the linear member 6 with the outer periphery 34 of the pulley 32 to the rotation axis a (i.e., equal to the radius of the pulley member 32).

In general, the tension of the coil spring 5 becomes proportional to its elastic deformation, i.e., the greater the elastic deformation of the coil spring, the greater the elastic force of the coil spring. In other words, when the pulley 32 rotationally stretches the coil spring 5 in the counterclockwise direction in fig. 1, the elastic force acting into the wire 6 is larger, whereas the elastic force acting into the wire 6 is smaller. With the present embodiment, the radius of the circular gear 31 and the weight of the load are constant, whereas the radius of the pulley 32 decreases at a predetermined rate when viewed clockwise in fig. 1 (i.e., the radius on the side shown to the right is larger than the radius on the side shown to the left) as shown in fig. 1. In other words, when the pulley 32 rotates counterclockwise, the elastic force of the coil spring 5 increases (the force applied to the pulley 32 by the wire 6 also increases), but the point of action connection of the wire 6 with the pulley 32 becomes leftward, that is, the radius of the pulley 32 decreases. Accordingly, the same situation occurs when the pulley 32 rotates clockwise, i.e., the spring force becomes smaller and smaller, but the radius of the pulley 32 becomes larger and larger. Therefore, if the change of the radius of the pulley 32 is designed appropriately, the second torque applied to the pulley 32 by the coil spring 5 can be always balanced with the first torque applied to the circular gear 31 by the gravity acting on the load, that is, the rotating wheel group 3 can convert the elastic force of the coil spring into a constant supporting force for the load or can be said to be the gravity which always keeps balanced with the load. In other words, the load is always in a weightless state due to the action of the vertical shock absorbing device according to the present embodiment.

When the vertical damping device for damping vertical vibrations from the support structure is subjected to vertical vibrations from the external environment, for example from the support structure. It should be noted that the vertical vibration herein refers to a vibration having a vertical component, that is, the vibration may be referred to as vertical vibration as long as the vibration has a component in the vertical direction, in other words, the macro motion direction of the vertical vibration is not necessarily the vertical direction, and may have an angle with the vertical direction. When the vertical vibration is, for example, a downward movement, the rotating wheel set 3 is displaced a certain distance downward in the vertical direction along with the supporting structure because the rotating shaft 2 in the vertical damping device is connected to the supporting structure 10. Because the circular gear 31 in the rotating wheel set 3 is meshed with the rack 41, the vertical displacement of the rotating wheel set 3 will correspondingly cause the circular gear 31 to rotate a certain angle in the clockwise direction to reach another angular position, and at the same time, will cause the rack 41 to displace a certain distance upwards under the driving of the circular gear 31 (i.e. to drive the load to move in the direction opposite to the vibration direction), because the above-mentioned gravity of the load can be kept balanced during the rotation of the rotating wheel set 3 in any direction, because the distance of the downward displacement of the rotating wheel set 3 is substantially equal to the distance of the upward displacement of the rack 41, the actual absolute position of the load in the vertical direction is not changed, i.e. the influence of the vibration of the external environment on the load is eliminated. In other words, because the vertical damping device of the present invention can drive the load to move in the opposite direction of the vibration direction via the rotation-linear motion conversion mechanism under the condition of keeping the gravity of the load balanced, the influence of the vibration of the external environment on the load is eliminated. The same situation can also occur when the vertical shock is an upward motion. Therefore, the technical personnel in the field can understand that the vertical damping device of the utility model can basically eliminate or isolate the influence of vertical up-and-down vibration on the load.

It is to be noted that, although in the present embodiment, a coil spring is used as the force generation mechanism, this is merely exemplary, and the force generation mechanism may also be a hydraulic damper capable of being extended or retracted in a linear direction or a coil spring and/or a hydraulic damper arranged in series or in parallel, as long as the force generation mechanism satisfies a relationship in which the tensile force is proportional to the amount of deformation thereof.

On this basis, as an advantageous improvement aspect, it is also desirable that the vertical damping device comprises an adjusting mechanism for adjusting the pretensioning force of the coil spring, thereby allowing the pretensioning force of the coil spring to be adjusted by a user during use of the vertical damping device to accommodate loads of different weights, which is advantageous for improving the versatility of the vertical damping device. Specifically, as shown in fig. 2, the adjusting mechanism includes a tubular sleeve 91 configured to receive the coil spring 5, and an end cap 92 fixedly supported at a rear end of the sleeve 91, with an internal thread provided at a central portion of the end cap 92. The adjustment mechanism further includes an adjustment member (not shown) fixedly connected to the other end of the coil spring, where the adjustment member is an adjustment screw threadedly engaged with the internal thread of the end cap 92 via its external thread. As shown in fig. 2, since the sleeve 91 is fixedly supported on the support structure via an upper flange portion on the side of the support structure 10 or the sleeve 91 may be formed integrally with the support structure, the fixed connection of the coil spring and the support structure can be achieved via the end cap 92 and the adjustment screw. Due to the threaded connection between the adjusting screw and the immovable end cap 92, during the use of the vertical shock absorber, a user can manually screw in or unscrew the adjusting screw relative to the end cap 92 so as to adjust the pre-tightening force of the coil spring 5 to adapt to loads with different weights. It will of course be understood that the end cap may also be screwed directly to the support structure and screwed in or out relative to the support structure to adjust the pretension of the helical spring, in which case it is allowed to arrange the helical spring in the support structure in a more flexible manner, for example it may be mounted obliquely or transversely, as long as it can be operatively connected to the balancing mechanism via a wire.

Further, as a preferable mode, the vertical shock absorbing device 1 may further include a guide mechanism 7 provided in parallel to the moving direction of the rotation-linear motion converting mechanism 4, wherein as shown in fig. 2, the guide mechanism 7 includes: at least one guide rail, preferably 2 guide rails, which are arranged parallel to the direction of movement of the rotation-linear motion conversion mechanism 4, extend parallel to the direction of movement and are seated at both ends thereof by mounting seats. Linear bearings 72 are respectively provided in the guide rails, and a carrier 73 fixedly connected to the rack 41 can be guided along the guide rails by means of the linear bearings 72. With this arrangement, the rack 41 can be moved vertically in a linearly guided manner without disengagement from the gear member 3, which is advantageous for the reliability of the vertical damping device 1.

In fig. 2 is also shown a vertical positioning device of a load according to the present invention, although as described above, the vertical damping device of the present invention can eliminate the adverse effect of the vibration of the external environment on the load, but in order to position the load in a desired vertical position more quickly and accurately, the vertical positioning device of the present invention may further comprise a position sensor (not shown) for measuring the position of the load, a controller (not shown) for receiving a signal of the position of the load from the position sensor, and a motor 8 connected to the rotating wheel set 3. And the position controller receives a signal of the position of the load from the position sensor and generates an output signal for controlling the action of the motor, and after receiving the output signal from the position controller, the motor acts to move the load for a certain distance along the direction opposite to the vibration direction, so that the load is positioned at a determined position in the vertical direction.

As described above, the load is always in a state where the gravity thereof is completely balanced or in a state where it is weightless, so that the motor does not need to bear the gravity of any load at the time of the rotational action in this case, and thus in the vertical position adjustment here, the micro motor or the small servo motor is feasible. The motor has the advantages of being fast and accurate in regulation and control, and meanwhile, the required energy consumption and heat dissipation capacity of the motor are small, so that unacceptable burden can not be caused to products such as a stabilizer or an unmanned aerial vehicle.

Fig. 3 and 4 show a further embodiment of the invention, in which most of the components are identical to those of the first embodiment, with the difference being the structure of the balancing mechanism and the rotary-linear motion conversion mechanism associated therewith. Accordingly, the same reference numerals are used for the same components.

As shown in fig. 3 and 4, unlike the first embodiment, in the present embodiment, the balance mechanism includes a balance 33 and a pulley 32 having a radius variable with angle at least in part, wherein the rotation-linear motion converting mechanism includes a sliding portion 331 fixedly provided at the outer periphery of the balance 33, wherein the sliding portion 331 is preferably a smooth-surfaced roller, a linear displacement member 42 having a slide groove 421 forming a sliding connection with the sliding portion 331, where the linear displacement member may be elongated and provided at the tip thereof with an external thread portion for connecting a load. As shown in fig. 3 to 4, during the rotational oscillation of the balance 33, the moving speed of the sliding portion 331 thereon can be orthogonally resolved, where the horizontal speed is Vx and the vertical speed is Vy. Therefore, during the rotation and oscillation of the balance 33, on one hand, the sliding portion 331 will generate a certain horizontal displacement in the sliding slot 421, and on the other hand, the sliding portion 331 will drive the linear displacement member 42 to move vertically. In other words, through the cooperation of the sliding portion 331 and the sliding groove 421, the balance 33 and the linear displacement member 42 can be equivalently formed into a crank-slider structure, thereby ensuring that the linear displacement member 42 only moves in the vertical direction, i.e., the rotational oscillation of the balance is converted into the linear movement of the linear displacement member. Preferably, the sliding portion 331 may be a roller, whereby undesired friction between the sliding portion 331 and the sliding groove 421 can be reduced as much as possible to ensure efficient motion transmission; the balance 33 and the pulley member 32 may here be separately manufactured and then arranged coaxially on the pivot shaft 2 in a rotationally fixed manner with respect to each other (e.g. fixedly connected to each other or glued), so as to allow both balance 33 and pulley member 32 to always remain co-rotating. It is of course also conceivable to form balance 33 and pulley 32 in one piece. Further, as a variant, it is also possible for the balance 33 to be replaced by a rocker with a sliding portion at the outer end, provided that it is ensured that the distance between the sliding portion and the pivot axis a is constant.

Also, since the position of the sliding portion 331 is fixed, the distance from the rotation axis a is constant throughout the swing. Meanwhile, since the slide portion 331 is embedded in the slide groove 421 of the linear displacement member 42 that carries a load, the weight of the load can apply a torque, which may be referred to as a first torque, to the balance 33 in the counterclockwise direction in fig. 4 with respect to the pivot shaft 2 via the contact of the slide portion 331 and the slide groove 421. Wherein the torque is equal to the product of the weight force of the load and the distance between the rotation-linear motion converting mechanism 4 and the pivot shaft 2 (i.e., the radius of the sliding portion 331 to the rotational center of the balance).

As in the exemplary embodiment shown in fig. 1 to 2, a force generating mechanism 5, here a helical spring 5 which can be extended or retracted in the vertical direction, is arranged below the pulley 32 opposite the linear displacement element 42 with respect to the pivot axis a. Wherein the lower end of the helical spring 5 is fixedly connected to the supporting structure (not shown), for example, it is likewise possible to fixedly connect the helical spring to the supporting structure in a pretension-adjustable manner. While the upper end of the helical spring 5 is operatively connected to the pulley 32 via a wire element 6, here for example a steel or nylon or carbon fiber wire, provided that it has a sufficient tensile strength. In order to facilitate guiding and deflecting the wire 6, a guide wheel, which may be an idler wheel having a smooth outer peripheral surface, is further provided near the pulley member 32. As shown in fig. 3-4, the wire 6 is guided along the outer periphery of the pulley 32 having a variable radius with angle. The pulley 32 in fig. 3-4 may have the same shape and function as the pulley 32 shown in fig. 1, and a detailed description thereof will not be repeated.

When the pulley 32 rotates in any direction, the linear member 6 is always in a state of force balance, i.e., the frictional force given to the linear member 6 by the outer periphery of the pulley 32 is equal to the tension of the linear member 6 (also equal to the elastic force of the coil spring 5). The linear element 6 will thus likewise impart a tangentially equally large force to the pulley element 32, under which a torque, which may be referred to as a second torque, will be exerted on the pulley element 32 in the clockwise direction in fig. 4 relative to the pivot axis 2. Wherein the torque is equal to the product of the elastic force in the force generating mechanism and the distance from the point of action connection of the linear member 6 with the outer periphery of the pulley member 32 to the axis of rotation 2, i.e., equal to the radius of the pulley member 32.

As described above, the second torque applied to the pulley 32 by the coil spring 5 can always balance the first torque applied to the balance 33 by the gravity acting on the load, as long as the change of the radius of the pulley 32 is properly designed, i.e., the balance mechanism shown in fig. 3 to 4 can also convert the elastic force of the coil spring into a constant supporting force for the load or can be referred to as a gravity force that always keeps balance of the load. In other words, the vertical shock absorbing device according to the present embodiment can also function to keep the load in a weightless state at all times.

As in the embodiment of fig. 1-2, the force generating mechanism may also be a hydraulic damping member that can be extended or retracted in a linear direction or a coil spring and/or a hydraulic damping member arranged in series or in parallel, as long as the force generating mechanism satisfies a relationship in which the tensile force is proportional to the amount of deformation thereof. Likewise, an adjustment mechanism as described above may also be provided in fig. 3-4, which allows the pretension of the helical spring to be adjusted by the user during use of the vertical damping device.

Likewise, as shown in fig. 3 to 4, the vertical damping device 1 may also include a guide mechanism 7 disposed parallel to the movement direction of the rotation-to-linear motion converting mechanism 4, so that the linear shifter 42 can move vertically in a linearly guided manner without coming off the balance 33, which is advantageous to the reliability of the vertical damping device 1.

Alternatively, as a modification, another type of force generating mechanism operatively connected to the balancing mechanism is shown in fig. 5. The balancing mechanism shown in fig. 5 has the same structure as the balancing mechanism of fig. 3-5, and will not be described again. In fig. 5, the force generation mechanism includes: a spiral spring 5A which can be wound or unwound in a spiral direction, a guide wheel 61A which is arranged coaxially with the spiral spring 5A, and a wire 6A which operatively connects the guide wheel to the balance mechanism. As shown in the figure, the spiral spring 5A is disposed below the guide wheel 61A and is fixedly connected to the bottom surface of the guide wheel 61A via its outer end portion, and the wire 6A is operatively connected to the balance mechanism in a manner guided by the guide wheel 61A. Meanwhile, the inner end of the spiral spring 5A is fixedly connected to a supporting structure so that the spiral spring can be wound or unwound along with the rotation of the balance mechanism. The force generating mechanism shown in fig. 5 has the advantage over the force generating mechanisms shown in fig. 1-4 of enabling a more compact arrangement and allowing installation in a small space. As a further improvement, an adjusting mechanism for adjusting the pretensioning force of the volute spring shown in fig. 5 can also be added to the volute spring, wherein the adjusting mechanism comprises a rotating shaft 93 fixedly connected to the other end (here, the inner end) of the volute spring, wherein the rotating shaft 93 can be connected to a worm wheel 94 rotatably positioned on the supporting structure (not shown), and a worm, not shown here, cooperating with the worm wheel 94, wherein both ends of the worm are rotatably supported on the supporting structure 10, respectively, so that the worm wheel 94 and the rotating shaft connected thereto can be driven by rotating the worm to adjust the pretensioning force of the volute spring 5A.

Fig. 6 to 7 likewise show a further pretension adjustment of the volute spring 5A, in which the same reference numerals are used for the same components. Wherein the adjusting mechanism here comprises: a ratchet wheel 95 fixedly connected to the other end (here, the inner end) of the spiral spring 5A, wherein the ratchet wheel 95 has a plurality of teeth grooves arranged at intervals in the circumferential direction, wherein the ratchet wheel 95 is coaxially arranged below the spiral spring 5A; and a pivotable pawl 96 fixedly mounted to the support structure 10 and engaged or disengaged with the ratchet wheel 95, where the pawl 96 is designed in an L-shape comprising a shorter section connected to the support structure 10 via a spring 98 and a longer section for engagement to a tooth slot on the outer periphery of the ratchet wheel 95. The shorter and longer sections have shaft holes at their junctions through which the pivot shaft 96 passes, thereby allowing the pawl 96 to pivot about the pivot shaft 96 to pivotally disengage the ratchet 95 or to pivotally engage the ratchet 95, wherein engagement of the pivotable pawl 96 to the ratchet 95 locks the volute spring 5A in an angular position having a predetermined preload.

Specifically, when a heavier load requires a greater preload on the volute 5A, the wire first rotates the ratchet 95 counterclockwise to allow the pawl 96 to disengage from the teeth on the ratchet 95, the pawl 96 is pressed by the user to prevent it from being urged by the spring 98 to interfere with the rotation of the ratchet, the pre-load on the volute 5A is then applied by rotating the ratchet 95 clockwise to the desired angle, and then the pawl 96 is released to return to engagement with the teeth on the ratchet 95 to fix the angle of the ratchet 95. When the load is light and the pretightening force of the volute spring 5A needs to be reduced, the pawl 96 is also disengaged to allow the ratchet wheel 95 to rotate anticlockwise, so that the angle of the ratchet wheel 95 can be adjusted bidirectionally, and the pretightening force of the volute spring is adjusted. Therefore, the pre-tightening force of the volute spring can be adjusted to adapt to loads with different weights.

It is also particularly desirable to note that although the balance mechanisms shown in connection with fig. 1-5 each carry a pulley, it is equally conceivable that the balance mechanism may be, for example, a lever comprising a first balance arm and a second balance arm connected to the first balance arm, wherein both the first balance arm and the second balance arm are pivotable relative to the axis of rotation a. The first balance arm may be operatively connected to the constant force spring. While the rotation-linear motion converting mechanism for vertically supporting the load is slidably connected with a sliding part such as shown in fig. 3-4 through a sliding groove provided thereon, the action of the lever allows a heavier load to be supported and to be in a weightless state by a smaller constant force spring. The sliding connection of the sliding portion and the slide groove allows the linear displacement member in the rotation-linear motion converting mechanism to slide vertically in upward and downward directions relative to the second balance arm 2 upon oscillation of the second balance arm, which also achieves the effect of bringing the load to move in the direction opposite to the direction of the vibration upon being subjected to vertical vibration. The advantages of such a balancing mechanism require fewer parts and are simpler in construction than the balancing mechanism described above.

In fig. 3-4 and 8, a vertical positioning device for a load according to the present invention is also shown, although as described above, the vertical damping device 1 of the present invention can eliminate the adverse effect of the vibration of the external environment on the load, but in order to position the load at a desired vertical position more quickly and accurately, the vertical positioning device of the present invention may further include a position sensor (not shown) for measuring the position of the load, a controller (not shown) for receiving a signal of the position of the load from the position sensor, and a motor 8 connected to the balancing mechanism. And the position controller receives a signal of the position of the load from the position sensor and generates an output signal for controlling the action of the motor, and after receiving the output signal from the position controller, the motor acts to move the load for a certain distance along the direction opposite to the vibration direction, so that the load is positioned at a determined position in the vertical direction. Further preferably, the vertical positioning device of the load may be provided with a handle member for being held by a user. It is also conceivable that the vertical positioning device of the load can also be mounted directly to an unmanned aerial vehicle, an unmanned vehicle or a vehicle or the like.

It will be appreciated that the above described vertical shock absorbing device for absorbing vertical shock from a support structure may be used in a stabilizer for an imaging device, such as but not limited to a hand-held stabilizer, a drone, an unmanned vehicle, etc. In the case where the stabilizer for the imaging apparatus is a hand-held stabilizer, the support structure may be, for example, a handle of the stabilizer for the user to hold, and at this time, vertical vibration generated when the user walks may be damped by the vertical damping means, so that the quality and effect of photographing can be secured even in the case where the user walks. Likewise, in the case where the stabilizer for the imaging device is a drone, the support structure may be, for example, a suspended pod of the drone or the like.

It will be appreciated that the vertical shock absorbing means described above for absorbing vertical shock from the support structure may be used in general for photographic equipment such as VR video capture robots or movie carriages and the like.

It is to be understood that while the specification has been described in terms of various embodiments, it is not intended that each embodiment comprises a separate embodiment, and such descriptions are provided for clarity only and should be taken as a whole by those skilled in the art, and that the embodiments may be combined to form other embodiments as will be apparent to those skilled in the art.

The above description is only exemplary of the present invention, and is not intended to limit the scope of the present invention. Without departing from the concept and principles of the present invention, equivalent changes, modifications and combinations that may be made by those skilled in the art should be considered within the scope of the present invention.

Claims (15)

1. A vertical shock absorbing device for absorbing vertical shock from a supporting structure, the vertical shock absorbing device being for supporting a load, the vertical shock absorbing device comprising:

a balancing device, comprising: a rotation shaft having a pivot axis and mounted on the support structure and a balancing mechanism rotatable about the rotation shaft;

a rotation-to-linear motion conversion mechanism vertically supporting the load, configured to be operatively connected to the counterbalance mechanism at a first distance from the pivot axis on one side thereof to apply a first torque to the counterbalance mechanism in a first rotational direction under the weight of the load;

a force generating mechanism configured to be operatively connected to the balance mechanism at a second distance from the pivot axis on the other side of the balance mechanism to apply a second torque to the balance mechanism in a second rotational direction opposite the first rotational direction under the force applied by the force generating mechanism, the force generating mechanism being fixedly connected at one end to the support structure;

when the balance mechanism is subjected to vertical vibration and is in different angular positions, the load is driven to move along the direction opposite to the vibration direction through the rotation-linear motion conversion mechanism under the condition of keeping the gravity for balancing the load when the balance mechanism rotates along any direction.

2. The vertical shock absorbing device of claim 1, wherein the counterbalance mechanism comprises: a circular gear and a pulley having an angle-variable radius at least in part, which are coaxially arranged, wherein the rotation-linear motion converting mechanism is configured to include a rack gear engaged with the circular gear.

3. The vertical shock absorbing device of claim 1, wherein the counterbalance mechanism comprises: the rotation-linear motion conversion mechanism comprises a sliding part fixedly arranged at the outer end of the swinging part, and a linear displacement part with a sliding chute in sliding connection with the sliding part, so that the rotation swing of the swinging part is converted into the linear motion of the linear displacement part.

4. The vertical shock absorbing device of claim 1, wherein the force generating mechanism comprises:

the spiral spring can be wound or unwound along the spiral direction;

a guide wheel disposed coaxially with the spiral spring;

and a wire member connecting the guide wheel to the balance mechanism,

wherein one end of the spiral spring is fixedly connected to the guide wheel and operatively connected to the balance mechanism via the linear member, and the other end of the spiral spring is fixedly connected to the support structure such that the spiral spring can be wound or unwound as the balance mechanism rotates, wherein the linear member is guided along an outer periphery of the balance mechanism.

5. The vertical shock absorbing device of claim 4, further comprising an adjustment mechanism for adjusting the preload of the volute spring, comprising:

the rotating shaft is fixedly connected with the other end of the spiral spring; and

the worm gear is rotatably positioned on the supporting structure and is connected with the rotating shaft, and the worm is matched with the worm gear, wherein the worm gear and the rotating shaft connected with the worm gear are driven by rotating the worm so as to adjust the pretightening force of the volute spring.

6. The vertical shock absorbing device of claim 4, further comprising an adjustment mechanism for adjusting the preload of the volute spring, comprising:

the ratchet wheel is fixedly connected with the other end of the spiral spring; and

a pivotable pawl fixedly mounted to the support structure and engaged with or disengaged from the ratchet wheel, wherein the pivotable pawl when engaged to the ratchet wheel locks the volute spring in an angular position having a predetermined preload force.

7. The vertical shock absorbing device of claim 1, wherein the force generating mechanism comprises: any one of a coil spring capable of being stretched or retracted in a linear direction, a hydraulic damper capable of being stretched or retracted in a linear direction, or a combination thereof, wherein one end of the force generating mechanism is fixedly connected to a linear member and is operatively connected to the balance mechanism via the linear member and the other end is fixedly connected to the support structure so that the force generating mechanism can be stretched or retracted with rotation of the balance mechanism, wherein the linear member is guided along an outer periphery of the balance mechanism.

8. The vertical shock absorbing device of claim 7, further comprising guide wheels for deflecting the line.

9. The vertical shock absorbing device of claim 7, further comprising a mechanism for adjusting the preload of the coil spring, comprising:

an adjusting screw which is screwed to the support structure and is fixedly connected to the other end of the helical spring, wherein the pretension of the helical spring is adjusted by screwing the adjusting screw in or out relative to the support structure.

10. The vertical shock absorbing device according to claim 1, further comprising a guide mechanism provided in parallel to a moving direction of the rotation-linear motion converting mechanism, wherein the guide mechanism comprises:

at least one guide rail provided in parallel to the moving direction of the rotation-linear motion converting mechanism;

at least one linear bearing arranged on the guide rail in a penetrating way; and

and the support can be guided and slide along the guide rail through the linear bearing, wherein the support is fixedly connected with the rotation-linear motion conversion mechanism so as to realize linear guide of the rotation-linear motion conversion mechanism.

11. A vertical positioning apparatus for a load, comprising a position sensor for measuring the position of the load, a position controller and a motor, wherein the position controller receives a signal from the position sensor of the position of the load and generates an output signal for controlling the action of the motor, wherein the positioning apparatus further comprises a vertical shock absorbing device according to any one of claims 1 to 10 for vertically supporting the load, wherein the motor is connected to the balancing mechanism to move the load in a direction opposite to the direction of vibration via the action of the motor, thereby positioning the load in a determined position in the vertical direction.

12. A stabilizer for an image forming apparatus, comprising a support structure and a vertical shock absorbing device connected to the support structure for vertically supporting the image forming apparatus, wherein the vertical shock absorbing device comprises:

a balancing device, comprising: a rotation shaft having a pivot axis and mounted on the support structure and a balancing mechanism rotatable about the rotation shaft;

a rotation-to-linear motion converting mechanism vertically supporting the image forming apparatus, configured to be operatively connected to the balance mechanism at a first distance from the pivot axis at one side of the balance mechanism to apply a first torque to the balance mechanism in a first rotational direction under the influence of gravity of the image forming apparatus;

a force generating mechanism configured to be operatively connected to the balance mechanism at a second distance from the pivot axis on the other side of the balance mechanism to apply a second torque to the balance mechanism in a second rotational direction opposite the first rotational direction under the force applied by the force generating mechanism, and the force generating mechanism is fixedly connected at one end to the support structure;

wherein when the balance mechanism is subjected to vertical vibration from the support structure to be in different angular positions, the image forming apparatus is driven to move in the opposite direction to the vibration direction via the rotation-linear motion conversion mechanism while keeping the balance of the gravity of the image forming apparatus when the balance mechanism is rotated in any direction.

13. The stabilizer of claim 12, further comprising:

a position sensor for measuring a position of the imaging device;

a controller for receiving a signal of a position of the imaging device from the position sensor; and

and the controller is used for controlling the motor to act according to the position information of the imaging device detected by the position sensor so as to drive the balance mechanism to rotate.

14. The stabilizer of claim 13, wherein: the sensor is an inertia measuring unit, and the controller controls the motor to drive the balance mechanism to rotate when the inertia measuring unit detects that the supporting structure generates vibration, so that the imaging device moves along the opposite direction of the vibration direction relative to the supporting structure, and the imaging device has a basically unchanged absolute position in the vertical direction.

15. A photographing apparatus comprising an imaging device, an axial stabilizing device for alleviating axial vibration of the imaging device, and a vertical damping device for alleviating the imaging device, wherein the vertical damping device is the vertical damping device according to any one of claims 1 to 10.