CN113606287B - Ultralow frequency metal shock absorber capable of eliminating initial static deformation - Google Patents
Ultralow frequency metal shock absorber capable of eliminating initial static deformation Download PDFInfo
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- CN113606287B CN113606287B CN202111152165.7A CN202111152165A CN113606287B CN 113606287 B CN113606287 B CN 113606287B CN 202111152165 A CN202111152165 A CN 202111152165A CN 113606287 B CN113606287 B CN 113606287B
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- pulley
- gear
- sliding block
- shock absorber
- spring
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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
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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
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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
- F16F15/067—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 wound 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
- F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
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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
- F16F2230/00—Purpose; Design features
- F16F2230/0011—Balancing, e.g. counterbalancing to produce static balance
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Dampers (AREA)
Abstract
The invention discloses an ultralow frequency metal shock absorber capable of eliminating initial static deformation, and belongs to the field of metal shock absorbers. The device comprises a shell, a balance support plate, an end cover A, an end cover B, a guide rail rack rod, an equipment platform, a rigidity equivalent conversion device and a zero displacement self-balancing device; the rigidity equivalent conversion device comprises a bull gear A, a pinion gear A, a bull gear B, a pinion gear B, a rotating shaft, a bull gear C, a force gain rod, an arc-shaped sliding block, a spring guide plate and a telescopic spring; the zero-displacement self-balancing device comprises a pulley A, a pulley B, a pulley E, a translational sliding block, a translational connecting rod, a pulley C, a pulley D, a static sliding block, a flexible rope B, a balance weight and a flexible rope A. The ultralow frequency metal shock absorber has a simple and reasonable structure, has static zero displacement, and realizes ultralow frequency inherent frequency by using the high-stiffness spring.
Description
Technical Field
The invention mainly relates to the field of metal shock absorbers, in particular to an ultralow frequency metal shock absorber capable of eliminating initial static deformation.
Background
The metal shock absorber for achieving shock absorption by adopting spring force is widely applied to engineering, and under the general condition, the smaller the rigidity of the spring is, the lower the natural frequency of a system is, and the better the shock absorption effect is; at the same time, the smaller the stiffness of the spring, the greater the initial static deformation of the system, resulting in a greater initial length of the metal spring. The natural frequency of the metal shock absorber in the prior art is usually more than 5Hz, so that the ultra-low frequency (the natural frequency is less than 5 Hz) shock absorption of low-frequency (5-10 Hz) exciting force in the external environment is difficult to realize; and the static initial displacement of the existing low-frequency shock absorber is too large, so that the overall height of the shock absorber is too high. Therefore, the ultra-low frequency shock absorber capable of eliminating the initial static deformation has a certain engineering application prospect.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: aiming at the technical problems in the prior art, the invention provides the ultralow frequency metal shock absorber which has a simple and reasonable structure, has static zero displacement and realizes ultralow frequency inherent frequency by utilizing a large-stiffness spring.
In order to solve the problems, the solution proposed by the invention is as follows: the utility model provides a can eliminate initial static deformation's ultralow frequency metal shock absorber, includes the shell, along the horizontal direction fixed install the inside balanced mounting panel of shell, fixed the installing respectively end cover A and the end cover B at shell both ends, the lower extreme is located the upper end is located in the shell is passed end cover A extends the guide rail rack bar that installs along the vertical direction outward, and fixed the installing is in guide rail rack bar upper end is used for installing the equipment platform by shock attenuation equipment.
The right side surface of the guide rail rack rod is provided with meshing teeth, and the left side surface of the guide rail rack rod is a smooth surface; the balance support plate is provided with a linear sliding groove along the horizontal direction.
The device also comprises a rigidity equivalent conversion device and a zero displacement self-balancing device which are arranged in the shell.
The rigidity equivalent conversion device comprises a large gear A, a small gear A, a large gear B, a small gear B and a rotating shaft which are arranged on the shell in a rotating mode, wherein a large gear C and a force gain rod which are arranged on the rotating shaft are fixedly arranged, the force gain rod is rotatably arranged, the arc-shaped sliding block is far away from one end of the rotating shaft, and a spring guide plate and a telescopic spring which are arranged on the end cover B are fixedly arranged.
The bull gear A and the pinion A are coaxially and synchronously rotatably arranged, and the bull gear B and the pinion B are coaxially and synchronously rotatably arranged; the rack gear A is meshed with the rack bar of the guide rail, the pinion A is externally meshed with the rack gear B, and the pinion B is externally meshed with the rack gear C; the spring guide plate is provided with an arc-shaped sliding groove which takes the rotating shaft as the center of a circle, the arc-shaped sliding block and the telescopic spring are installed in the arc-shaped sliding groove, and two ends of the telescopic spring are respectively connected with the arc-shaped sliding block and the spring guide plate.
The zero displacement self-balancing device comprises a pulley A, a pulley B and a pulley E which are rotatably arranged on a balance support plate, a translation sliding block which is slidably arranged on a linear sliding groove, a translation connecting rod which is fixedly arranged on the translation sliding block along the horizontal direction, a pulley C and a pulley D which are rotatably arranged on the translation connecting rod, a static sliding block which is fixedly arranged at the right end of the balance support plate and is in sliding fit with a guide rail rack rod, a flexible rope B of which one end is connected with the lower end of the guide rail rack rod and the other end bypasses the pulley E and is connected with the translation sliding block, a balance weight, and a flexible rope A of which one end is connected with the balance weight and the other end sequentially bypasses the pulley A, the pulley D, the pulley B and the pulley C and is connected with the center of the pulley B.
Furthermore, the bull gear A, the bull gear B and the bull gear C are sector gears.
Further, the radius of the bull gear a is not less than twice the radius of the pinion gear a; the radius of the bull gear B is not less than twice the radius of the pinion gear B; the radius of the bull gear C is not less than twice of the radius of the circular arc chute.
Further, the part of the flexible rope B between the pulley E and the translation sliding block is arranged along the horizontal direction.
Further, the extension spring is a metal spiral tension and compression spring.
Further, when the equipment platform is in a static balance state after the equipment to be damped is installed, the deformation amount of the telescopic spring is zero.
Further, the gravity of the balance weight and the total weight of the equipment platform and the damped equipment form a balance system.
Compared with the prior art, the invention has the following advantages and beneficial effects: the ultralow frequency metal shock absorber capable of eliminating initial static deformation is provided with a zero displacement self-balancing device, an equipment platform and a shock-absorbing device can be balanced at any position under the action of self weight by arranging a balance weight and five pulleys, the initial static deformation in a static balance state is eliminated under the condition that the equivalent rigidity of the whole system is not influenced, and the static zero displacement is realized; the invention is also provided with a rigidity equivalent conversion device, and a large-rigidity extension spring can be converted into the system equivalent rigidity of ultralow frequency through two groups of large gears and small gears which rotate coaxially, a force gain rod and a circular arc-shaped sliding chute, so that the metal shock absorber has ultralow frequency inherent frequency. Therefore, the ultralow frequency metal shock absorber has a simple and reasonable structure, has static zero displacement, and realizes ultralow frequency natural frequency by using the high-stiffness spring.
Drawings
FIG. 1 is a schematic view illustrating the structural principle of an ultra-low frequency metal damper capable of eliminating initial static deformation according to the present invention.
In the figure, 10-equipment platform, 11-rack bar; 12-end cap a; 13-a housing; 14-end cap B; 15-a balance support plate; 151-linear chute; 21-gearwheel a; 22-pinion a; 23-gearwheel B; 24-pinion B; 25-gearwheel C; 26-a rotating shaft; 27-a spring guide plate; 28-a telescopic spring; 29-arc slider; 210-force gain lever; 31-pulley a; 32-pulley B; 33-Pulley C; 34-pulley D; 35-translational connecting rod; 36-translation slide block; 37-pulley E; 38-flexible cord a; 39-balance weight; 310 — stationary slide; 311-flexible cord B.
Detailed Description
The invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.
As shown in FIG. 1, the ultra-low frequency metal shock absorber capable of eliminating initial static deformation of the present invention comprises a housing 13, a balance support plate 15 fixedly installed in the housing 13 along a horizontal direction, end caps A12 and B14 fixedly installed at two ends of the housing 13, a rack bar 11 with a lower end located in the housing 13, an upper end passing through the end cap A12 and extending outward along a vertical direction, and an equipment platform 10 fixedly installed at the upper end of the rack bar 11 for installing equipment to be damped.
The right side surface of the guide rail rack bar 11 is provided with meshing teeth, and the left side surface is a smooth surface; the balance support plate 15 is provided with a linear sliding groove 151 along the horizontal direction.
And also comprises a rigidity equivalent conversion device and a zero displacement self-balancing device which are arranged in the shell 13.
The rigidity equivalent conversion device comprises a big gear A21, a small gear A22, a big gear B23, a small gear B24, a rotating shaft 26, a big gear C25 and a force gain rod 210 which are fixedly arranged on the rotating shaft 26, an arc-shaped sliding block 29 which is rotatably arranged on the force gain rod 210 and is far away from one end of the rotating shaft 26, a spring guide plate 27 and a telescopic spring 28 which are fixedly arranged on an end cover B14.
The bull gear A21 and the pinion gear A22 are coaxially and synchronously rotatably arranged, and the bull gear B23 and the pinion gear B24 are coaxially and synchronously rotatably arranged; the large gear A21 is meshed with the guide rail rack bar 11, the small gear A22 is meshed with the large gear B23, and the small gear B24 is meshed with the large gear C25; the spring guide plate 27 is provided with a circular arc chute with the rotating shaft 26 as the center of circle, an arc slide block 29 and a telescopic spring 28 are arranged in the circular arc chute, and two ends of the telescopic spring 28 are respectively connected with the arc slide block 29 and the spring guide plate 27.
The zero displacement self-balancing device comprises a pulley A31, a pulley B32 and a pulley E37 which are rotatably arranged on a balance support plate 15, a translation sliding block 36 which is slidably arranged on a linear sliding groove 151, a translation connecting rod 35 which is fixedly arranged on the translation sliding block 36 along the horizontal direction, a pulley C33 and a pulley D34 which are rotatably arranged on the translation connecting rod 35, a static sliding block 310 which is fixedly arranged at the right end of the balance support plate 15 and is in sliding fit with a guide rail rack rod 11, a flexible rope B311 which is connected with the lower end of the guide rail rack rod 11 at one end and passes around the pulley E37 at the other end and is connected with the translation sliding block 36, a balance weight 39, and a flexible rope A38 which is connected with the balance weight 39 at one end and sequentially passes around the pulley A31, the pulley D34, the pulley B32 and the pulley C33 at the other end and is connected with the center of the pulley B32. The zero displacement self-balancing device can enable the equipment platform 10 with the shock-absorbing equipment to be installed to take any height point as a static balance position in a zero-deformation state of the extension spring 28, so that the overall design height of the shock absorber can be reduced.
Preferably, the bull gear a21, the bull gear B23 and the bull gear C25 are sector gears.
Preferably, the radius of the large gear a21 is not less than twice the radius of the small gear a 22; the radius of the bull gear B23 is no less than twice the radius of the pinion gear B24; the radius of the large gear C25 is not less than twice the radius of the circular arc chute.
Preferably, the portion of the flexible rope B311 between the pulley E37 and the translation slider 36 is installed in the horizontal direction, so that the pulling force of the flexible rope B311 is fully used as the main driving force of the translation slider 36, and the upward acting force component of the flexible rope B311 on the equipment platform 10 is equal to the total weight of the equipment platform 10 and the damped equipment.
Preferably, the extension spring 28 is a metal coil tension and compression spring.
Preferably, the amount of deformation of the extension springs 28 is zero when the apparatus platform 10 is in a static equilibrium state after installation of the damped apparatus.
Preferably, the weight of the counterweight 39 and the total weight of the apparatus platform 10 and the damped apparatus comprise a balance system.
The working principle of the zero displacement self-balancing device is as follows: the pulley C33, the pulley D34, the translational connecting rod 35 and the translational sliding block 36 form a movable pulley block. Since the weight of the balance weight 39 and the total weight of the equipment platform 10 and the damped equipment form a balance system, although the included angle exists between the flexible rope B311 and the rack bar 11, when the equipment platform 10 moves up and down near the balance position, the change value of the tension in the flexible rope B311 caused by the change of the included angle is negligible compared with the initial tension value of the flexible rope B311, and since the tension in the flexible rope a38 is equal to one fourth of the tension of the flexible rope B311, the change value of the tension in the flexible rope a38 is completely negligible compared with the weight of the balance weight 39, the equipment platform 10 and the damped equipment can form a dynamic self-balance system with the balance weight 39, and even if the equipment platform 10 moves up and down after the damped equipment is installed, the deformation of the telescopic spring 28 is not influenced by the weight. Therefore, the zero-displacement self-balancing device of the invention not only eliminates the vertical displacement generated by the self-weight of the damped equipment and the equipment platform 10, but also can always keep dynamic self-balancing in the damping process, and eliminates the requirement of the static balance position on the initial deformation of the spring.
The working principle of the rigidity equivalent conversion device is as follows: the radius ratio of the big gear A21 and the small gear A22 is not set as
The radius ratio of the big gear B23 to the small gear B24 is
The radius ratio of the large gear C25 to the arc chute is
The device platform 10 is excited at an external force
Is moved and displaced under the action of
The deformation of the expansion spring 28 along the direction of the circular arc chute is
Corresponding spring force of
I.e. the spring has a stiffness of
。
When the equipment platform 10 moves downwards, the bull gear A21 and the pinion gear A22 rotate anticlockwise, the bull gear B23 and the pinion gear B24 rotate clockwise, the bull gear C25 and the force gain rod 210 rotate anticlockwise, and the extension spring 28 is shortened; when the equipment platform 10 moves upward, the bull gear a21 and the pinion gear a22 rotate clockwise, the bull gear B23 and the pinion gear B24 rotate counterclockwise, the bull gear C25 and the force amplification lever 210 rotate clockwise, and the extension spring 28 lengthens. From the energy conservation, the length change of the expansion spring 28 along the arc chute direction
Displacement from the lifting movement of the equipment platform 10
Satisfy the relation:
(ii) a The displacement can be known according to the meshing transmission theory
And the amount of displacement
Satisfy the relation
From the formula of equivalent stiffness
It can be seen that the equivalent stiffness of the shock absorber of the present invention
. Therefore, the rigidity equivalent transformation device of the invention can transform one rigidity into
Is turned to be smaller than
The system stiffness of (1). Natural frequency of the system
Proportional to system equivalent stiffness
The square root of (i), i.e.
. Therefore, when the rigidity of the extension spring meets the condition that the frequency is 5-10Hz, the natural frequency of the system is changed into 0.625-1.25Hz after the damper is installed on the damped equipment, and the ultra-low frequency damping far less than 5Hz is realized.
The above is only a specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that are not thought of through creative efforts should fall within the scope of the present invention.
Claims (6)
1. An ultra-low frequency metal shock absorber capable of eliminating initial static deformation comprises a shell (13), a balance support plate (15) fixedly arranged in the shell (13) along the horizontal direction, end covers A (12) and B (14) fixedly arranged at two ends of the shell (13) respectively, a guide rail rack rod (11) with the lower end positioned in the shell (13), the upper end penetrating through the end cover A (12) and extending to the outside along the vertical direction, and an equipment platform (10) fixedly arranged at the upper end of the guide rail rack rod (11) and used for installing damped equipment; the method is characterized in that:
the right side surface of the guide rail rack rod (11) is provided with meshing teeth, and the left side surface is a smooth surface; a linear sliding groove (151) along the horizontal direction is formed in the balance support plate (15);
the device also comprises a rigidity equivalent conversion device and a zero displacement self-balancing device which are arranged in the shell (13);
the rigidity equivalent conversion device comprises a big gear A (21), a small gear A (22), a big gear B (23), a small gear B (24) and a rotating shaft (26) which are rotatably arranged on the shell (13), a big gear C (25) and a force gain rod (210) which are fixedly arranged on the rotating shaft (26), an arc-shaped sliding block (29) which is rotatably arranged on the force gain rod (210) and is far away from one end of the rotating shaft (26), a spring guide plate (27) which is fixedly arranged on the end cover B (14), and a telescopic spring (28);
the bull gear A (21) and the pinion gear A (22) are coaxially and synchronously rotationally mounted, and the bull gear B (23) and the pinion gear B (24) are coaxially and synchronously rotationally mounted; the rack gear A (21) is meshed with the rack bar (11) of the guide rail, the pinion A (22) is externally meshed with the rack gear B (23), and the pinion B (24) is externally meshed with the rack gear C (25); the spring guide plate (27) is provided with an arc-shaped sliding groove taking the rotating shaft (26) as a circle center, the arc-shaped sliding groove is internally provided with the arc-shaped sliding block (29) and the telescopic spring (28), and two ends of the telescopic spring (28) are respectively connected with the arc-shaped sliding block (29) and the spring guide plate (27);
the zero-displacement self-balancing device comprises a pulley A (31), a pulley B (32) and a pulley E (37) which are rotatably arranged on a balance support plate (15), a translation sliding block (36) which is slidably arranged on a linear sliding groove (151), a translation connecting rod (35) which is fixedly arranged on the translation sliding block (36) along the horizontal direction, a pulley C (33) and a pulley D (34) which are rotatably arranged on the translation connecting rod (35), a static sliding block (310) which is fixedly arranged at the right end of the balance support plate (15) and is in sliding fit with a guide rail rack rod (11), a flexible rope B (311) with one end connected with the lower end of the guide rail rack rod (11) and the other end connected with the pulley E (37) and connected with the translation sliding block (36), a balance weight (39), one end of the balance weight (39) and the other end connected with the balance weight (39) are sequentially wound around the pulley A (31), A flexible rope A (38) connected to the center of the pulley B (32), a pulley D (34), a pulley B (32), and a pulley C (33).
2. The ultra-low frequency metal shock absorber capable of eliminating initial static deformation according to claim 1, wherein: the bull gear A (21), the bull gear B (23) and the bull gear C (25) are all sector gears.
3. The ultra-low frequency metal shock absorber capable of eliminating initial static deformation according to claim 1, wherein: the radius of the bull gear A (21) is not less than twice the radius of the pinion gear A (22); the radius of the bull gear B (23) is not less than twice the radius of the pinion gear B (24); the radius of the big gear C (25) is not less than twice of the radius of the circular arc sliding chute.
4. The ultra-low frequency metal shock absorber capable of eliminating initial static deformation according to claim 1, wherein: the part of the flexible rope B (311) between the pulley E (37) and the translational sliding block (36) is arranged along the horizontal direction.
5. The ultra-low frequency metal shock absorber capable of eliminating initial static deformation according to claim 1, wherein: the extension spring (28) is a metal spiral tension and compression spring.
6. The ultra-low frequency metal shock absorber capable of eliminating initial static deformation according to claim 1, wherein: when the equipment platform (10) provided with the damped equipment is in a static balance state, the deformation amount of the telescopic spring (28) is zero, and the gravity of the balance weight (39), the total weight of the equipment platform (10) and the damped equipment form a balance system.
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| CN202111152165.7A CN113606287B (en) | 2021-09-29 | 2021-09-29 | Ultralow frequency metal shock absorber capable of eliminating initial static deformation |
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| CN202111152165.7A CN113606287B (en) | 2021-09-29 | 2021-09-29 | Ultralow frequency metal shock absorber capable of eliminating initial static deformation |
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| CN113606287B true CN113606287B (en) | 2021-11-30 |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3895770A (en) * | 1972-07-15 | 1975-07-22 | Olympus Optical Co | Weight balancing mechanism for use in precision elevating and lowering means |
| GB2085390A (en) * | 1980-09-30 | 1982-04-28 | Zeiss Jena Veb Carl | Apparatus for driving and counter-balancing vertically displaceable structural units |
| US6474637B1 (en) * | 2000-12-19 | 2002-11-05 | Unisys Corporation | Adaptive flag weight for document handling apparatus |
| CN102927197A (en) * | 2012-11-20 | 2013-02-13 | 东北石油大学 | Composite balance energy-saving oil extractor for double speed reducer |
| CN205370522U (en) * | 2016-01-26 | 2016-07-06 | 西安石油大学 | Half gear drives rack reciprocating motion's beam -pumping unit |
| CN207813983U (en) * | 2018-01-27 | 2018-09-04 | 河北博一泵业有限公司 | A kind of lift self-control self-priming water pump |
| CN110259862A (en) * | 2019-06-28 | 2019-09-20 | 长沙理工大学 | A kind of ultralow frequency vibration isolator and its design method |
-
2021
- 2021-09-29 CN CN202111152165.7A patent/CN113606287B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3895770A (en) * | 1972-07-15 | 1975-07-22 | Olympus Optical Co | Weight balancing mechanism for use in precision elevating and lowering means |
| GB2085390A (en) * | 1980-09-30 | 1982-04-28 | Zeiss Jena Veb Carl | Apparatus for driving and counter-balancing vertically displaceable structural units |
| US6474637B1 (en) * | 2000-12-19 | 2002-11-05 | Unisys Corporation | Adaptive flag weight for document handling apparatus |
| CN102927197A (en) * | 2012-11-20 | 2013-02-13 | 东北石油大学 | Composite balance energy-saving oil extractor for double speed reducer |
| CN205370522U (en) * | 2016-01-26 | 2016-07-06 | 西安石油大学 | Half gear drives rack reciprocating motion's beam -pumping unit |
| CN207813983U (en) * | 2018-01-27 | 2018-09-04 | 河北博一泵业有限公司 | A kind of lift self-control self-priming water pump |
| CN110259862A (en) * | 2019-06-28 | 2019-09-20 | 长沙理工大学 | A kind of ultralow frequency vibration isolator and its design method |
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| Publication number | Publication date |
|---|---|
| CN113606287A (en) | 2021-11-05 |
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