CN115095599B - Double-shaft cross-bar hinge with large deflection angle and strong vibration resistance - Google Patents
Double-shaft cross-bar hinge with large deflection angle and strong vibration resistance Download PDFInfo
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- CN115095599B CN115095599B CN202210916069.3A CN202210916069A CN115095599B CN 115095599 B CN115095599 B CN 115095599B CN 202210916069 A CN202210916069 A CN 202210916069A CN 115095599 B CN115095599 B CN 115095599B
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- 230000007246 mechanism Effects 0.000 claims abstract description 93
- 235000014676 Phragmites communis Nutrition 0.000 claims abstract description 70
- 230000003068 static effect Effects 0.000 claims abstract description 4
- 244000273256 Phragmites communis Species 0.000 claims description 19
- 229910000831 Steel Inorganic materials 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/12—Pivotal connections incorporating flexible connections, e.g. leaf springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/073—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only leaf springs
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
Abstract
The invention discloses a double-shaft crossed spring hinge with large deflection angle and strong vibration resistance, which comprises an upper mounting seat, a flexible reed serving as a deflection mechanism, a reversing seat, a lower mounting seat and a locking gasket for locking the flexible reed on the upper mounting seat, the reversing seat and the lower mounting seat. The upper mounting seat and the lower mounting seat are respectively connected with the dynamic end and the static end of an external mechanism; the reversing seat realizes the two-axis rotation function of the cross spring hinge; the flexible reed is a key structure of the cross spring hinge, so that the angle deflection function of the cross spring hinge is realized; the locking gasket realizes the locking and positioning function of the reed. The cross-shaped cross spring hinge in the scheme is mainly suitable for a biaxial deflection scene under the working condition of large-angle deflection and high vibration.
Description
Technical Field
The invention belongs to the field of micro-nano quick positioning, and particularly relates to a double-shaft crossed spring hinge with large deflection angle and strong vibration resistance.
Background
The cross spring hinge is used in the fields of active optical systems, precision manufacturing, micro-nano operation and the like, and the angle deflection capability and the vibration resistance capability of the cross spring hinge can directly influence the precision of an external mechanism connected with the cross spring hinge. Because of the insufficient deflection angle and insufficient vibration resistance in the prior art of cross-spring hinges used in products, which results in product functions, it is desirable to provide a cross-spring hinge with a large deflection angle and high vibration resistance.
Disclosure of Invention
The invention discloses a double-shaft cross spring hinge with large deflection angle and strong vibration resistance, which is used for solving the problems of insufficient deflection angle and insufficient vibration resistance of the conventional cross spring hinge.
The technical scheme of the invention is as follows:
The invention provides a double-shaft cross spring hinge with large deflection angle and strong vibration resistance, which comprises the following components:
An upper mounting seat for connecting with the movable end of the external mechanism,
A lower mounting seat used for connecting with the static end of the external mechanism,
The reversing seat is arranged between the upper mounting seat and the lower mounting seat,
Two groups of first angle deflection mechanisms assembled and fixed with the upper mounting seat and the reversing seat, and
Two groups of second angle deflection mechanisms are assembled and fixed with the lower mounting seat and the reversing seat;
The first angle deflection mechanism and the second angle deflection mechanism comprise two flexible reeds with collinear deflection shafts and arranged in a crisscross manner;
The deflection axes of the first angle deflection mechanism and the second angle deflection mechanism are vertically crossed;
the deflection axes of the two groups of first angle deflection mechanisms are collinear, and the deflection axes of the two groups of second angle deflection mechanisms are collinear.
Preferably, the double-shaft crossed spring hinge further comprises:
and a locking mechanism arranged on each flexible reed, wherein the locking mechanism is used for locking the corresponding flexible reed on a part assembled with the corresponding flexible reed.
Preferably, the locking mechanism is a locking washer, and the parts assembled with the flexible reeds are fixed with the locking washer.
Preferably, the reversing seat comprises:
A reversing seat body,
A first assembling end formed at the upper end of the reversing seat body and assembled with two groups of the second angle deflection mechanisms, and
The second assembly ends are formed at the lower end of the reversing seat body and assembled with the two groups of first angle deflection mechanisms;
the orthographic projections of the first and second mounting ends are arranged in a crisscross configuration.
Preferably, the first assembly end consists of two first assembly seats which extend outwards symmetrically along the positive and negative directions of the X axis at the upper end of the reversing seat body, and the second assembly end consists of two second assembly seats which extend outwards symmetrically along the positive and negative directions of the Y axis at the lower end of the reversing seat body;
Two third assembly seats extend outwards symmetrically along the positive and negative directions of the Y axis on the upper mounting seat, and two fourth assembly seats extend outwards symmetrically along the positive and negative directions of the X axis on the lower mounting seat;
a group of second angle deflection mechanisms are assembled between the first assembly seat and a fourth assembly seat corresponding to the first assembly seat;
a group of first angle deflection mechanisms are assembled between the second assembly seat and a third assembly seat corresponding to the second assembly seat;
The X-axis and the Y-axis are perpendicular to the horizontal plane.
Preferably, the first mount and the fourth mount each have: a mounting interface for engaging the second angular deflection mechanism and a locking mechanism mounted thereon;
The second mount and the third mount each have: a mounting interface for engaging the first angular deflection mechanism and a locking mechanism mounted thereon;
The mounting interface of each assembly seat is two inclined planes which are perpendicular to each other.
Preferably, the maximum deflection angles of the first and second angle deflection mechanisms are each 15 °.
Preferably, the upper mounting seat and the lower mounting seat are both provided with limiting sections for limiting the reversing seat and adjusting the position of the reversing seat.
Preferably, the flexible reed adopts a processing technology of one-time cutting and forming after stacking a plurality of sheets.
The invention has the following advantages:
The cross spring hinge adopts the flexible reed as a deflection structure, the flexible reed is made of cold-rolled formed steel plate, the surface quality is high, and the processing damage surface is a non-working surface, so that the cutting damage to the working surface of the flexible reed is avoided. The working surface is not damaged, so that the flexible reed can bear high-strength vibration without damage.
The two flexible reeds are arranged in a crisscross manner when the first angle deflection mechanisms and the second angle deflection mechanisms are assembled, the first angle deflection mechanisms and the second angle deflection mechanisms are symmetrically arranged on two symmetrical mounting interfaces of the reversing seat, and the second angle deflection mechanisms are symmetrically arranged on the other two symmetrical mounting interfaces of the reversing seat, so that the crisscross symmetrical arrangement of the crisscross reed hinge is realized. The stress moments of the symmetrically arranged crisscross spring hinges compensate each other when the crisscross spring hinges deflect, so that the stress of the flexible spring leaves is uniformly distributed on the whole working surface of the flexible spring leaves, and stress concentration is avoided; the flexible reed is of a flat plate structure, and the whole working surface can be bent and has uniform rigidity, so that the flexible reed can bear large-angle deflection within 15 degrees.
The processing of the flexible reed overcomes the principle weaknesses that the traditional flexible hinge formed by cutting the space curve has extremely low local rigidity and the other parts have extremely high rigidity to deflect so as to lead to small deflection angle and easy fracture.
The flexible reed adopts a processing technology of stacking a plurality of sheets and cutting and forming at one time; all flexible reeds required by one cross reed hinge can be finished by single processing, and the consistency of the tolerance of the flexible reeds required by each cross reed hinge is ensured. The deflection center of the assembled flexible reed has high coaxiality, so the deflection center is stable, and the repetition precision is high.
Drawings
FIG. 1 is a three-dimensional expanded view of a cross-bar hinge;
FIG. 2 is a Y-direction elevation view of the cross spring hinge;
FIG. 3 is an X-direction elevation view of a cross-bar hinge;
Fig. 4 is a top mounting view of a cross-bar hinge.
Detailed Description
Referring to fig. 1 to 4, the present embodiment provides a double-shaft cross spring hinge having a large deflection angle and a strong vibration resistance, which has an ability to angularly deflect along two axes.
The double-shaft cross spring hinge includes: an upper mounting seat 1, a reversing seat 3, a lower mounting seat 2 and a flexible reed.
The upper mount 1 may be machined to the desired form.
The flexible reed is used as an angle deflection mechanism for realizing deflection of the double-shaft crossed reed hinge. Wherein, two sets of symmetrically arranged first angle deflection mechanisms 4 are arranged between the upper mounting seat 1 and the reversing seat 3, and two sets of symmetrically arranged second angle deflection mechanisms 5 are arranged between the lower mounting seat 2 and the reversing seat 3.
Each group of first angle deflection mechanisms 4 and each group of second angle deflection mechanisms 5 are composed of two flexible reeds which are arranged in a crisscross manner, and deflection axes of the two flexible reeds are collinear.
As shown in fig. 1, the deflection axes of the two first angular deflection mechanisms 4 are collinear, the deflection axes of the two second angular deflection mechanisms 5 are collinear, and the deflection axes of the first angular deflection mechanisms 4 and the second angular deflection mechanisms 5 vertically intersect. That is, the four sets of angle deflection mechanisms are distributed in four directions of the reversing seat.
The front projection of the reversing seat 3 along the Z direction (vertical direction) is in a cross shape, the upper end of the reversing seat body 31 is respectively and outwards symmetrically extended with a first assembling seat 32 along the positive direction and the reverse direction of the X axis, the lower end of the reversing seat body is respectively and outwards symmetrically extended with a second assembling seat 33 along the positive direction and the reverse direction of the Y axis, the two first assembling seats 32 form first assembling ends for assembling the reversing seat 3 with the two groups of second angle deflection mechanisms 5, and the two second assembling seats 33 form second assembling ends for assembling the reversing seat 3 with the two groups of first angle deflection mechanisms 4. The X axis and the Y axis are vertical in the horizontal direction.
The upper mounting seat 1 is respectively and symmetrically extended with a third assembling seat 11 along the forward direction and the reverse direction of the Y axis, and the lower mounting seat 2 is respectively and symmetrically extended with a fourth assembling seat 21 along the forward direction and the reverse direction of the X axis. A set of second angular deflection mechanisms 5 is connected between a first mount 32 and a fourth mount 21, and a set of first angular deflection mechanisms 4 is connected between a second mount 33 and a third mount 11.
In the present embodiment, the first to fourth mount blocks 32 to 21 are required to have a mount interface slope that is fitted and fitted with the flexible reed. Specifically, the first inclined surface 321 of the first mount 32 is disposed obliquely downward, the first inclined surface 331 of the second mount 33 is disposed obliquely upward, the first inclined surface 111 of the third mount 11 is disposed obliquely downward, the first inclined surface 211 of the fourth mount 21 is disposed obliquely upward, the first inclined surface 321 of the first mount 32 is parallel to the first inclined surface 211 of the fourth mount 21, and the first inclined surface 331 of the second mount 33 and the first inclined surface 111 of the third mount 11 are parallel.
The flexible reeds are thin slices with the same thickness, and the upper side and the lower side of each flexible reed are respectively provided with a corresponding screw hole which is in screw connection fixation with the first inclined plane of the reversing seat 3. Wherein, for a group of second angle deflection mechanisms 5, the flexible reed positioned at the upper side of the two flexible reeds is jointed and connected with the first inclined surface 321 of the first assembling seat 32, and the flexible reed positioned at the lower side is jointed and connected with the first inclined surface 211 of the fourth assembling seat 21. For the first angular deflection mechanism 4, the flexible reed located at the upper side of the two flexible reeds is attached and connected to the first inclined surface 111 of the third assembly seat 11, and the flexible reed located at the lower side of the two flexible reeds is attached and connected to the first inclined surface 331 of the second assembly seat 33.
In this embodiment, the connection between the upper mount 1, the reversing mount 3 and the lower mount 2 is achieved by means of flexible reeds. When the external mechanism needs to deflect around the X axis, the external mechanism drives the upper mounting seat 1 to move, the movement of the upper mounting seat 1 drives the first angle deflection mechanism 4 to synchronously rotate, and then drives the second angle deflection mechanism 5 on the reversing seat 3 to rotate, and the second angle deflection mechanism 5 immediately deflects at an angle relative to the X axis; when the external mechanism needs to deflect around the Y axis, the external mechanism drives the upper mounting seat 1 to move, and then drives the first angle deflection mechanism 4 on the reversing seat 3 to rotate, and the first angle deflection mechanism 4 immediately deflects at an angle relative to the Y axis.
Considering that when the flexible reed is assembled with the upper mounting seat 1, the lower mounting seat 2 and the reversing seat 3 by means of the screws 7, the problem that the cross reed hinge may deflect unstably after repeated use is caused due to insufficient single-sided assembly stability, therefore, the locking mechanism 6 for locking the flexible reed with the upper mounting seat 1, the lower mounting seat 2 and the reversing seat 3 is added, and the locking mechanism 6 is a locking gasket vertically arranged on each flexible reed. Wherein, two flexible reeds of each group of angle deflection mechanism are provided with two locking gaskets with opposite directions, the first assembling seat 32 to the fourth assembling seat 21 are provided with second inclined planes which are locked with the locking gaskets, and the first inclined planes and the second inclined planes of the assembling seats are vertically arranged in space to form an installation interface. Specifically, for the second angle deflection mechanism 5 assembled between the lower mounting seat 2 and the reversing seat 3, the locking gasket assembled on the upper surface of the flexible reed positioned on the upper side of the two flexible reeds is locked by a screw after being attached to the second inclined surface 322 of the first assembling seat 32, the locking gasket assembled on the lower surface of the flexible reed positioned on the lower side is locked by a screw 7 after being attached to the second inclined surface 212 of the fourth assembling seat 21, and after the assembly is completed, the upper end of the second angle deflection mechanism 5 and the first assembling seat 32 are in cross locking, and the lower end of the second angle deflection mechanism is in cross locking with the fourth assembling seat 21. Similarly, for the first angle deflection mechanism 4 assembled between the upper mounting seat 1 and the reversing seat 3, the cross-shaped assembly locking between the flexible reed and the upper mounting seat 1 and the reversing seat 3 is realized by adopting the same structure. Therefore, the assembly stability between the flexible spring and each part can be improved, and the reuse precision of the external mechanism is high after the external mechanism is assembled and locked with the cross spring hinge.
The working principle of the cross-shaped cross spring hinge is as follows:
The movable end (rotating end) of the external product is fixedly connected with the upper mounting seat 1 through 4 screws, and the static end (fixed end) of the external product is connected with the lower mounting seat 2 through 4 screws. After connection and fixation, the two-axis rotation function of the whole product can be realized.
The cross spring hinge adopts the flexible reed as a deflection structure, the flexible reed is made of cold-rolled formed steel plate, the surface quality is high, and the processing damage surface is a non-working surface, so that the cutting damage to the working surface of the flexible reed is avoided. The working surface is not damaged, so that the flexible reed can bear high-strength vibration without damage.
The two flexible reeds are arranged in a crisscross manner when the first angle deflection mechanisms 4 and the second angle deflection mechanisms 5 are assembled, the first angle deflection mechanisms 4 are symmetrically arranged on two symmetrical mounting interfaces of the reversing seat, and the second angle deflection mechanisms 5 are symmetrically arranged on the other two symmetrical mounting interfaces of the reversing seat, so that the crisscross symmetrical arrangement of the crisscross reed hinge is realized. The stress moments of the symmetrically arranged crisscross spring hinges compensate each other when the crisscross spring hinges deflect, so that the stress of the flexible spring leaves is uniformly distributed on the whole working surface of the flexible spring leaves, and stress concentration is avoided; the flexible reed is of a flat plate structure, and the whole working surface can be bent and has uniform rigidity, so that the flexible reed can bear large-angle deflection within 15 degrees.
The processing of the flexible reed overcomes the principle weaknesses that the traditional flexible hinge formed by cutting the space curve has extremely low local rigidity and the other parts have extremely high rigidity to deflect so as to lead to small deflection angle and easy fracture.
The flexible reed adopts a processing technology of stacking a plurality of sheets and cutting and forming at one time; all flexible reeds required by one cross reed hinge can be finished by single processing, and the consistency of the tolerance of the flexible reeds required by each cross reed hinge is ensured. The deflection center of the assembled flexible reed has high coaxiality, so the deflection center is stable, and the repetition precision is high.
Claims (8)
1. A dual-axis cross spring hinge having a large deflection angle and a high vibration resistance, the dual-axis cross spring hinge comprising:
an upper mounting seat (1) used for being connected with the movable end of an external mechanism,
A lower mounting seat (2) used for being connected with the static end of an external mechanism,
The reversing seat (3) is arranged between the upper mounting seat (1) and the lower mounting seat (2),
Two groups of first angle deflection mechanisms (4) which are assembled and fixed with the upper mounting seat (1) and the reversing seat (3), and
Two groups of second angle deflection mechanisms (5) which are assembled and fixed with the lower mounting seat (2) and the reversing seat (3);
The first angle deflection mechanism (4) and the second angle deflection mechanism (5) comprise two flexible reeds with collinear deflection shafts and arranged in a crisscross manner;
the deflection axes of the first angle deflection mechanism (4) and the second angle deflection mechanism (5) are vertically crossed;
The deflection axes of the two groups of first angle deflection mechanisms (4) are collinear, and the deflection axes of the two groups of second angle deflection mechanisms (5) are collinear.
2. The dual-axis cross spring hinge having a large deflection angle and a high vibration resistance according to claim 1, further comprising:
And a locking mechanism (6) arranged on each flexible reed, wherein the locking mechanism (6) realizes locking of the corresponding flexible reed on a part assembled with the corresponding flexible reed.
3. A double-shaft cross spring hinge with high deflection angle and high vibration resistance according to claim 2, characterized in that the locking mechanism (6) is a locking washer, and the parts assembled with the flexible reeds are fixed with the locking washer.
4. The dual-axis cross spring hinge having a large deflection angle and a high vibration resistance according to claim 1, wherein the reversing seat comprises:
A reversing seat body (31),
A first assembling end which is formed at the upper end of the reversing seat body (31) and is assembled with two groups of second angle deflection mechanisms (5), and
The second assembly end is formed at the lower end of the reversing seat body (31) and assembled with the two groups of first angle deflection mechanisms (4);
the orthographic projections of the first and second mounting ends are arranged in a crisscross configuration.
5. The double-shaft crossed spring hinge with high vibration resistance at a large deflection angle according to claim 4, wherein the first assembly end consists of two first assembly seats (32) symmetrically extending outwards along the positive and negative directions of the X axis at the upper end of the reversing seat body (31), and the second assembly end consists of two second assembly seats (33) symmetrically extending outwards along the positive and negative directions of the Y axis at the lower end of the reversing seat body (31);
two third assembly seats (11) are symmetrically extended outwards along the positive and negative directions of the Y axis on the upper mounting seat (1), and two fourth assembly seats (21) are symmetrically extended outwards along the positive and negative directions of the X axis on the lower mounting seat (2);
a group of second angle deflection mechanisms (5) are arranged between a first assembly seat (32) and a fourth assembly seat (21) corresponding to the position of the first assembly seat;
A group of first angle deflection mechanisms (4) are arranged between a second assembly seat (33) and a third assembly seat (11) corresponding to the position of the second assembly seat;
The X-axis and the Y-axis are perpendicular to the horizontal plane.
6. Double-shaft cross spring hinge with high deflection angle vibration resistance according to claim 5, characterized in that the first mount (32) and the fourth mount (21) each have: a mounting interface which is attached to the second angle deflection mechanism (5) and the locking mechanism (6) assembled on the second angle deflection mechanism;
The second mount (33) and the third mount (11) each have: a mounting interface which is attached to the first angle deflection mechanism (4) and the locking mechanism (6) assembled on the first angle deflection mechanism;
The mounting interface of each assembly seat is two inclined planes which are perpendicular to each other.
7. Double-shaft cross spring hinge with high deflection angle vibration resistance according to claim 1, characterized in that the deflection maximum angle of the first angle deflection mechanism (4) and the second angle deflection mechanism (5) is 15 °.
8. The dual-axis cross spring hinge with high deflection angle and high vibration resistance according to claim 1,
The upper mounting seat (1) and the lower mounting seat (2) are respectively provided with a limiting section for limiting the reversing seat (3) and adjusting the position of the reversing seat (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210916069.3A CN115095599B (en) | 2022-08-01 | 2022-08-01 | Double-shaft cross-bar hinge with large deflection angle and strong vibration resistance |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210916069.3A CN115095599B (en) | 2022-08-01 | 2022-08-01 | Double-shaft cross-bar hinge with large deflection angle and strong vibration resistance |
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| Publication Number | Publication Date |
|---|---|
| CN115095599A CN115095599A (en) | 2022-09-23 |
| CN115095599B true CN115095599B (en) | 2024-04-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210916069.3A Active CN115095599B (en) | 2022-08-01 | 2022-08-01 | Double-shaft cross-bar hinge with large deflection angle and strong vibration resistance |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115903170B (en) * | 2022-12-01 | 2024-01-26 | 中国科学院长春光学精密机械与物理研究所 | Double-shaft flexible supporting structure of large-caliber strip-shaped reflecting mirror |
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|---|---|---|---|---|
| CN1718479A (en) * | 2004-07-09 | 2006-01-11 | 株式会社村上开明堂 | Member tilting mechanism |
| DE102014006727B3 (en) * | 2014-05-08 | 2015-10-22 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Solid-state joint and its use for exo- and endoprostheses as well as in the form of an orthotic joint |
| CN207554560U (en) * | 2017-12-14 | 2018-06-29 | 王洪福 | A kind of single load bearing universal joint hook switch linkage for realizing the rotation of two axis |
| CN108873320A (en) * | 2018-08-18 | 2018-11-23 | 重庆巅慧科技有限公司 | A kind of two-dimensional rapid control reflector |
| CN213117121U (en) * | 2020-08-18 | 2021-05-04 | 西安海康普德智能装备有限公司 | Composite hinge with three rotational degrees of freedom |
-
2022
- 2022-08-01 CN CN202210916069.3A patent/CN115095599B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1718479A (en) * | 2004-07-09 | 2006-01-11 | 株式会社村上开明堂 | Member tilting mechanism |
| DE102014006727B3 (en) * | 2014-05-08 | 2015-10-22 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Solid-state joint and its use for exo- and endoprostheses as well as in the form of an orthotic joint |
| CN207554560U (en) * | 2017-12-14 | 2018-06-29 | 王洪福 | A kind of single load bearing universal joint hook switch linkage for realizing the rotation of two axis |
| CN108873320A (en) * | 2018-08-18 | 2018-11-23 | 重庆巅慧科技有限公司 | A kind of two-dimensional rapid control reflector |
| CN213117121U (en) * | 2020-08-18 | 2021-05-04 | 西安海康普德智能装备有限公司 | Composite hinge with three rotational degrees of freedom |
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|---|---|
| CN115095599A (en) | 2022-09-23 |
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