CN113294478B - Damping force is directly proportional to liquid damper of displacement - Google Patents
Damping force is directly proportional to liquid damper of displacement Download PDFInfo
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- CN113294478B CN113294478B CN202110669890.5A CN202110669890A CN113294478B CN 113294478 B CN113294478 B CN 113294478B CN 202110669890 A CN202110669890 A CN 202110669890A CN 113294478 B CN113294478 B CN 113294478B
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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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
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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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
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Abstract
The invention discloses a liquid damper with damping force proportional to displacement, and belongs to the technical field of liquid dampers. The device comprises a threaded cylinder body, an end cover A, an end cover B and a threaded piston rod; the middle part of the threaded piston rod is provided with external threads, and the two ends of the threaded piston rod are provided with polished rods; the interior of the threaded cylinder body is also provided with a self-rotation damping device, four planet damping devices and a gear axial positioning device; the autorotation damping device comprises a threaded gear, a U-shaped cylinder A and a U-shaped cylinder B; the right end of the U-shaped cylinder A is provided with a fixed three-blade plate A, and the inner wall of the U-shaped cylinder B is provided with a sliding three-blade plate A; the planetary damping device comprises a planetary gear, a U-shaped cylinder C and a U-shaped cylinder D; the right end of the U-shaped cylinder C is provided with a fixed three-blade plate B, and the inner wall of the U-shaped cylinder D is provided with a sliding three-blade plate B. The liquid damper is simple and reasonable in structure, changes the damping force by changing the volume and the mass of the damping liquid in the rotary motion, and the damping force is in direct proportion to the displacement.
Description
Technical Field
The invention mainly relates to the technical field of liquid dampers, in particular to a liquid damper with damping force proportional to displacement.
Background
The liquid damper is an intelligent shock-absorbing instrument with a wide application range, and damping fluid flows in a throttling opening through the motion of a piston to generate damping force, so that the adjustment of the damping force mainly changes the flow or viscous absorption of the damping fluid. The damper in the prior art has certain disadvantages: a wide range of damping forces cannot be generated and the magnitude of the damping force has no correlation with the displacement of the piston rod. Therefore, the liquid damper with the damping force proportional to the displacement of the piston rod and a wide damping force range is designed, and has very important application value.
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 liquid damper which is simple and reasonable in structure, realizes the change of the damping force by changing the volume and the mass of the damping liquid in the rotary motion, and has the damping force in direct proportion to the displacement.
In order to solve the problems, the solution proposed by the invention is as follows: the utility model provides a damping force is directly proportional to liquid damper of displacement, is equipped with the cylindrical hollow screw cylinder body of internal thread including the inner wall, install in the end cover A and the end cover B at both ends about the screw cylinder body, the left end is located inside the screw cylinder body, the right-hand member passes end cover B extends to the outside threaded piston rod of screw cylinder body.
The middle part of the threaded piston rod is provided with an external thread, and the two ends of the threaded piston rod are provided with polished rods; the interior of the threaded cylinder body is also provided with an autorotation damping device, four planetary damping devices which have the same structure and can revolve around the autorotation damping device, and a gear axial positioning device for axially positioning the autorotation damping device; the planet dampers are uniformly distributed along the circumferential direction of the autorotation damping device.
The autorotation damping device comprises a threaded gear arranged on the external thread of the threaded piston rod and internally provided with an internal thread, a U-shaped cylinder A fixedly connected with the threaded gear at the right end, and a U-shaped cylinder B with the right end extending into the U-shaped cylinder A and capable of sliding along the axis direction of the threaded piston rod.
The inner wall of the U-shaped cylinder A is in sliding contact with the outer wall of the U-shaped cylinder B; the left end polish rod of the threaded piston rod is rotationally connected with the left end of the U-shaped cylinder B; the right end of the U-shaped cylinder A is provided with a fixed three-blade plate A, a gap A for the U-shaped cylinder B to pass through is reserved between the fixed three-blade plate A and the inner wall of the U-shaped cylinder A, and the length of the fixed three-blade plate A is equal to the axial depth of the U-shaped cylinder A; the inner wall of the U-shaped cylinder B is provided with a sliding three-blade plate A, the length of the sliding three-blade plate A is equal to the axial depth of the U-shaped cylinder B, and gaps B are reserved between the sliding three-blade plate A and the fixed three-blade plate A as well as between the fixed three-blade plate A and the threaded piston rod; the sliding three-blade plate A is in sliding contact with the fixed three-blade plate A.
The left end of the U-shaped cylinder B is positioned outside the U-shaped cylinder A, and a plurality of throttling ports A allowing damping fluid to flow are formed in the U-shaped cylinder B; a support A is fixedly arranged at the left end of the U-shaped cylinder B; the inner wall of the U-shaped cylinder A and the outer wall of the threaded piston rod form a basic rotating cavity A, and the inner wall of the U-shaped cylinder B and the outer wall of the threaded piston rod form an extended rotating cavity A.
The planetary damping device comprises a planetary gear, a U-shaped cylinder C and a U-shaped cylinder D, wherein the planetary gear is simultaneously in threaded engagement transmission with the external thread of the threaded gear and the thread in the threaded cylinder body, the right end of the U-shaped cylinder C is fixedly connected with the planetary gear, and the right end of the U-shaped cylinder D extends into the U-shaped cylinder C and can slide along the axis direction of the threaded piston rod.
The inner wall of the U-shaped cylinder C is in sliding contact with the outer wall of the U-shaped cylinder D; a fixed three-blade plate B is arranged at the right end of the U-shaped cylinder C, a gap C for the U-shaped cylinder D to pass through is reserved between the fixed three-blade plate B and the inner wall of the U-shaped cylinder C, and the length of the fixed three-blade plate B is equal to the axial depth of the U-shaped cylinder C; the inner wall of the U-shaped cylinder D is provided with a sliding three-blade plate B, and the length of the sliding three-blade plate B is equal to the axial depth of the U-shaped cylinder D; the sliding three-blade plate B is in sliding contact with the fixed three-blade plate B.
The left end of the U-shaped cylinder D is positioned outside the U-shaped cylinder C, and a plurality of throttling ports B allowing damping fluid to flow are formed in the U-shaped cylinder C; the left end of the U-shaped cylinder D is rotatably provided with a support column B; the inner cavity of the U-shaped cylinder C is a basic rotating cavity B, and the U-shaped cylinder C is an extended rotating cavity B.
The gear axial positioning device comprises a support plate fixedly arranged in the threaded cylinder body, wherein the left end of the support plate is fixedly arranged on the right end face of the threaded gear, the right end of the support plate penetrates through the support plate and is rotatably arranged on the hollow sleeve on the support plate, a thrust plate A and a thrust plate B which are fixedly arranged on the hollow sleeve and are respectively positioned on the left side and the right side of the support plate, a thrust bearing A between the thrust plate A and the support plate, and a thrust bearing B between the support plate and the thrust plate B.
The threaded cylinder is characterized in that a cross frame rod is further arranged inside the threaded cylinder body, the left end of the strut A is fixedly arranged in the middle of the cross frame rod, and the left end of the strut B is fixedly arranged at the end part of a branch of the cross frame rod.
A liquid cavity filled with damping liquid is formed between the end cover A and the support plate inside the threaded cylinder body, and the damping liquid in the liquid cavity can flow left and right through the throttling port A and the throttling port B.
Compared with the prior art, the invention has the following advantages and beneficial effects: the liquid damper with damping force proportional to displacement is provided with the gear circumferential positioning device, so that linear motion of the threaded piston rod is converted into rotary motion of damping liquid; the U-shaped cylinder is internally provided with a fixed three-blade plate and a sliding three-blade plate, and the damping liquid is driven to synchronously rotate along with the U-shaped cylinder to form rotary liquid damping force; the telescopic motion of the threaded piston rod in the invention can not only generate the rotation of the damping liquid, but also change the volume and the mass of the damping liquid in the basic rotating cavity and the expansion rotating cavity, thereby obviously changing the magnitude of the damping force. Therefore, the liquid damper is simple and reasonable in structure, the damping force is changed by changing the volume and the mass of the damping liquid in the rotary motion, and the damping force is in direct proportion to the displacement.
Drawings
Fig. 1 is a schematic diagram of the structural principle of a liquid damper with damping force proportional to displacement according to the present invention.
Fig. 2 is a schematic cross-sectional view a-a of fig. 1.
Fig. 3 is a schematic cross-sectional view of B-B in fig. 1.
In the figure, 10-screw cylinder; 11-end cap a; 12-end cap B; 13-a threaded piston rod; 14 — a liquid chamber; 21-a support plate; 22-thrust plate a; 23-thrust plate B; 24-a thrust bearing a; 25-a thrust bearing B; 26-a hollow sleeve; 31-a screw gear; 32-a U-shaped cylinder A; 321-fixing three-blade plate A; 33-a U-shaped cylinder B; 331-orifice a; 332 — sliding three-leaf plate a; 34-basic rotating chamber a; 35-expanding the rotating cavity a; 36-pillar a; 41-a planetary gear; 42-U-shaped cylinder C; 421-fixing three-blade plate B; 43-U-shaped cylinder D; 431-orifice B; 432-sliding three-leaf plate B; 44 — basic rotation chamber B; 45-expanding the rotating cavity B; 46-strut B; 5-a cross frame rod.
Detailed Description
The invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.
Referring to fig. 1 and 2, the liquid damper with damping force proportional to displacement according to the present invention includes a cylindrical hollow screw cylinder 10 having an inner wall provided with an internal thread, end caps a11 and B12 installed at left and right ends of the screw cylinder 10, and a threaded piston rod 13 having a left end located inside the screw cylinder 10 and a right end extending to the outside of the screw cylinder 10 through the end cap B12.
The middle part of the threaded piston rod 13 is provided with external threads, and the two ends are polished rods; the interior of the threaded cylinder body 10 is also provided with an autorotation damping device, four planetary damping devices which have the same structure and can revolve around the autorotation damping device, and a gear axial positioning device for axially positioning the autorotation damping device; the planet dampers are uniformly distributed along the circumferential direction of the autorotation damping device.
The rotation damping device comprises a threaded gear 31 arranged on the external thread of the threaded piston rod 13 and internally provided with an internal thread, a U-shaped cylinder A32 with the right end fixedly connected with the threaded gear 31, and a U-shaped cylinder B33 with the right end extending into the U-shaped cylinder A32 and capable of sliding along the axial direction of the threaded piston rod 13.
Referring to fig. 1 and 3, the inner wall of the U-shaped cylinder a32 is in sliding contact with the outer wall of the U-shaped cylinder B33; the left end polish rod of the threaded piston rod 13 is rotationally connected with the left end of the U-shaped cylinder B33; the right end of the U-shaped cylinder A32 is provided with a fixed three-blade plate A321, a gap A for the U-shaped cylinder B33 to pass through is reserved between the fixed three-blade plate A321 and the inner wall of the U-shaped cylinder A32, and the length of the fixed three-blade plate A321 is equal to the axial depth of the U-shaped cylinder A32; the inner wall of the U-shaped cylinder B33 is provided with a sliding three-blade plate A332, the length of the sliding three-blade plate A332 is equal to the axial depth of the U-shaped cylinder B33, and gaps B are reserved between the sliding three-blade plate A332 and the fixed three-blade plate A321 and the threaded piston rod 13; the sliding trilobe a332 is in sliding contact with the fixed trilobe a 321. When the threaded piston rod 13 moves leftwards, the U-shaped cylinder B33 is pushed leftwards, so that the U-shaped cylinder B33 slides leftwards relative to the U-shaped cylinder A32 and gradually withdraws from the U-shaped cylinder A32, and meanwhile, the sliding three-leaf plate A332 also slides leftwards relative to the fixed three-leaf plate A321; when the threaded piston rod 13 moves to the right, the U-shaped cylinder B33 is pulled to move to the right, so that the U-shaped cylinder B33 slides to the right relative to the U-shaped cylinder A32 and gradually enters the inside of the U-shaped cylinder A32, and meanwhile, the sliding three-leaf plate A332 also slides to the right relative to the fixed three-leaf plate A321. The U-shaped cylinder A32 rotates to drive the fixed three-blade plate A321 to rotate, and further the sliding three-blade plate A332 and the U-shaped cylinder B33 are pushed to rotate synchronously.
The left end of the U-shaped cylinder B33 is positioned outside the U-shaped cylinder A32, and a plurality of throttling ports A331 allowing damping fluid to flow are formed in the U-shaped cylinder B33; the left end of the U-shaped cylinder B33 is fixedly provided with a support A36; the inner wall of the U-shaped cylinder A32 and the outer wall of the threaded piston rod 13 form a basic rotating cavity A34, and the inner wall of the U-shaped cylinder B33 and the outer wall of the threaded piston rod 13 form an extended rotating cavity A35. When the threaded piston rod 13 moves leftwards, the U-shaped cylinder B33 is driven to move leftwards, and damping fluid gradually flows into the expansion rotating cavity A35 from the outside of the U-shaped cylinder 33 through the throttling port A331; when the threaded piston rod 13 moves to the right, the U-shaped cylinder B33 is driven to move to the right, and the damping fluid gradually flows into the outside of the U-shaped cylinder 33 from the expansion rotating cavity A35 through the throttling port A331.
The planetary damping device comprises a planetary gear 41 which is simultaneously meshed with the external thread of the threaded gear 31 and the internal thread of the threaded cylinder body 10 for transmission, a U-shaped cylinder C42 with the right end fixedly connected with the planetary gear 41, and a U-shaped cylinder D43 with the right end extending into the U-shaped cylinder C42 and capable of sliding along the axial direction of the threaded piston rod 13. The screw gear 31 rotates to bring the planetary gear 41 to roll along the screw thread of the inner wall of the screw cylinder 10, so that the U-shaped cylinder C42 and the U-shaped cylinder D43 synchronously revolve around the screw piston rod 13 and rotate around the axis of the planetary gear 41.
Referring to fig. 1 and 3, the inner wall of the U-shaped cylinder C42 is in sliding contact with the outer wall of the U-shaped cylinder D43; the right end of the U-shaped cylinder C42 is provided with a fixed three-blade plate B421, a gap C for the U-shaped cylinder D43 to pass through is reserved between the fixed three-blade plate B421 and the inner wall of the U-shaped cylinder C42, and the length of the fixed three-blade plate B421 is equal to the axial depth of the U-shaped cylinder C42; the inner wall of the U-shaped cylinder D43 is provided with a sliding three-blade plate B432, and the length of the sliding three-blade plate B432 is equal to the axial depth of the U-shaped cylinder D43; the sliding three-leaf B432 is in sliding contact with the fixed three-leaf B421.
The left end of the U-shaped cylinder D43 is positioned outside the U-shaped cylinder C42, and a plurality of throttling ports B431 allowing damping fluid to flow are formed in the U-shaped cylinder D43; the left end of the U-shaped cylinder D43 is rotatably provided with a support column B46; the inner cavity of the U-shaped cylinder C42 is a basic rotating cavity B44, and the U-shaped cylinder C43 is an extended rotating cavity B45. The U-shaped cylinder B43 moves leftwards, the damping fluid flows from the outer side of the U-shaped cylinder B43 to the inside of the expanded rotating cavity B45 through the throttling port B431, and the damping fluid in the basic rotating cavity B44 and the expanded rotating cavity B45 is more and more; the U-shaped cylinder B43 moves rightward, the damping fluid flows from the expanding rotating chamber B45 to the outside of the U-shaped cylinder B43 through the orifice B431, and the damping fluid in the basic rotating chamber B44 and the expanding rotating chamber B45 becomes less and less.
Gear axial positioning device installs in the inside mounting plate 21 of screw cylinder body 10 including the fixing, the left end is fixed to be installed on screw gear 31 right-hand member face, the right-hand member passes mounting plate 21 and rotates and installs the hollow sleeve 26 on mounting plate 21, the fixing is installed on hollow sleeve 26, be located thrust plate A22 and thrust plate B23 of the mounting plate 21 left and right sides respectively, install thrust bearing A24 between thrust plate A22 and mounting plate 21, install thrust bearing B25 between mounting plate 21 and thrust plate B23. When the threaded piston rod 13 moves leftwards under the action of external force, the threaded gear 31 and the hollow sleeve 26 simultaneously receive the acting force leftwards from the threaded piston rod 13, and at the moment, the thrust plate B23 is pressed on the support plate 21 through the thrust bearing B25, so that the threaded gear 31 is prevented from moving leftwards, the threaded gear 31 cannot move leftwards but rotates, and the left positioning of the threaded gear 31 is realized; when the threaded piston rod 13 is moved rightwards by external force, the threaded gear 31 and the hollow sleeve 26 are simultaneously applied with the rightwards acting force from the threaded piston rod 13, and the thrust plate A22 is pressed on the bracket plate 21 through the thrust bearing A24, so that the threaded gear 31 is prevented from moving rightwards, the threaded gear 31 cannot move rightwards but can only rotate, and the right positioning of the threaded gear 31 is realized.
A cross frame rod is further arranged inside the threaded cylinder 10, the left end of the strut A36 is fixedly arranged in the middle of the cross frame rod 5, and the left end of the strut B46 is fixedly arranged at the branch end of the cross frame rod 5. The threaded piston rod 13 moves leftwards, drives the U-shaped cylinder B33 to move leftwards, further pushes the cross rod 5 to move leftwards through the support A36, the cross rod 5 moves leftwards, and pulls the U-shaped cylinder D43 to move leftwards through the support B46, so that the U-shaped cylinder D43 slides leftwards relative to the U-shaped cylinder C42, and meanwhile, the sliding three-leaf plate B432 slides leftwards relative to the fixed three-leaf plate B421. The U-shaped cylinder C42 rotates to drive the fixed three-blade plate B421 to rotate, and further pushes the sliding three-blade plate B432 and the U-shaped cylinder D43 to rotate synchronously.
The interior of the screw cylinder 10 between the end cover A11 and the bracket plate 21 forms a liquid chamber 14 filled with damping liquid, and the damping liquid in the liquid chamber 14 can flow left and right through a throttling port A331 and a throttling port B431 to enter and exit the expansion rotation chamber A35 and the protection rotation chamber B45.
Damping force increasing principle: the threaded piston rod 13 moves leftwards, pushes the U-shaped cylinder B33 to move leftwards, and further pulls the U-shaped cylinder D43 to move leftwards through the cross rod 5; the U-shaped cylinder B33 moves leftwards, and the damping fluid in the basic rotating chamber A34 and the expansion rotating chamber A35 is gradually increased; the U-shaped cylinder D43 moves leftwards, and the damping fluid in the basic rotating chamber B44 and the expanding rotating chamber B45 is gradually increased; due to the axial positioning of the threaded gear 31, when the threaded piston rod 13 moves leftwards, the threaded gear 31 rotates forwards and drives the planet gear 41 to rotate, so that the damping fluid in the basic rotating cavity A34 and the expansion rotating cavity A35 is driven to rotate around the axial direction of the threaded gear 31 respectively, and the damping fluid in the basic rotating cavity B44 and the expansion rotating cavity B45 simultaneously revolves and rotates; the damping force increases gradually as the threaded piston rod 13 moves to the left causing more and more damping fluid to rotate.
Damping force reduction principle: the threaded piston rod 13 moves rightwards, pulls the U-shaped cylinder B33 to move rightwards, and then pushes the U-shaped cylinder D43 to move rightwards through the cross frame rod 5; the U-shaped cylinder B33 moves rightwards, and the damping fluid in the basic rotating chamber A34 and the expansion rotating chamber A35 gradually decreases; the U-shaped cylinder D43 moves to the right, and the damping fluid in the basic rotating chamber B44 and the expanding rotating chamber B45 also gradually decreases; due to the axial positioning of the threaded gear 31, when the threaded piston rod 13 moves rightwards, the threaded gear 31 rotates reversely and drives the planet gear 41 to rotate, so that the damping fluid in the basic rotating cavity A34 and the expansion rotating cavity A35 is driven to rotate around the axial direction of the threaded gear 31 respectively, and the damping fluid in the basic rotating cavity B44 and the expansion rotating cavity B45 simultaneously revolves and rotates; the damping force is gradually reduced as less and less damping fluid is turned by the movement of the threaded piston rod 13 to the right.
The principle of the formation of the main damping force is as follows: the damping force is composed of two parts of a throttling port (comprising a throttling port A331 and a throttling port B431) flowing damping force and a damping fluid rotating damping force, wherein the damping fluid rotating damping force is far larger than the throttling port flowing damping force, so that the damping force is approximately equal to the damping fluid rotating damping force in the process of moving the threaded piston rod 13 left and right. Due to the existence of the sliding three-vane A332 and the fixed three-vane A321, the damping fluid in the expanding rotary cavity A35 and the basic rotary cavity A34 synchronously rotates along with the rotation of the threaded gear 31, so that a part of damping force is formed in the expanding rotary cavity A35 and the basic rotary cavity A34; due to the existence of the sliding three-blade B432 and the fixed three-blade B421, the damping fluid in the expanding rotary cavity B45 and the basic rotary cavity B44 synchronously rotates along with the rotation of the planetary gear 41, so that another part of damping force is formed in the expanding rotary cavity B45 and the basic rotary cavity B44; the two parts of the damping force generally constitute the damping fluid rotational damping force.
The working process of the invention is as follows: the right end of the threaded piston rod 13 is used as a displacement zero reference point, and the leftward movement is the positive direction of the displacement. The threaded piston rod 13 moves leftwards, namely gradually retracts into the threaded cylinder body 10, more and more damping fluid rotates in the U-shaped cylinder A32 and the U-shaped cylinder B33, the damping force is larger and larger, and meanwhile, more and more damping fluid rotates in the U-shaped cylinder C42 and the U-shaped cylinder D43, the damping force is larger and larger, so that the damping force and the leftward displacement of the threaded piston rod 13 are increased linearly; conversely, when the threaded piston rod 13 moves to the right, i.e., gradually extends outward from the threaded cylinder 10, the damping fluid in the U-shaped cylinder a32 and the U-shaped cylinder B33 rotates less and less, and the damping force is smaller and less, and at the same time, the damping fluid in the U-shaped cylinder C42 and the U-shaped cylinder D43 rotates less and less, so that the damping force is linearly reduced with the reduction of the displacement amount of the threaded piston rod 13.
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 (1)
1. The utility model provides a damping force is directly proportional to liquid damper of displacement, is equipped with the cylindrical hollow screw cylinder body (10) of internal thread including the inner wall, install in end cover A (11) and end cover B (12) at both ends about screw cylinder body (10), the left end is located inside, the right-hand member of screw cylinder body (10) pass end cover B (12) extend to screw piston rod (13) of screw cylinder body (10) outside, its characterized in that:
the middle part of the threaded piston rod (13) is provided with an external thread, and the two ends are provided with polished rods; the threaded cylinder body (10) is also internally provided with an autorotation damping device, four planetary damping devices which have the same structure and can revolve around the autorotation damping device, and a gear axial positioning device for axially positioning the autorotation damping device; the planet damping devices are uniformly distributed along the circumferential direction of the autorotation damping device;
the autorotation damping device comprises a threaded gear (31) which is arranged on the external thread of the threaded piston rod (13) and is internally provided with an internal thread, a U-shaped cylinder A (32) with the right end fixedly connected with the threaded gear (31), and a U-shaped cylinder B (33) with the right end extending into the U-shaped cylinder A (32) and capable of sliding along the axial direction of the threaded piston rod (13);
the inner wall of the U-shaped cylinder A (32) is in sliding contact with the outer wall of the U-shaped cylinder B (33); the left end polish rod of the threaded piston rod (13) is rotationally connected with the left end of the U-shaped cylinder B (33); a fixed three-blade plate A (321) is arranged at the right end of the U-shaped cylinder A (32), a gap A for the U-shaped cylinder B (33) to pass through is reserved between the fixed three-blade plate A (321) and the inner wall of the U-shaped cylinder A (32), and the length of the fixed three-blade plate A (321) is equal to the axial depth of the U-shaped cylinder A (32); a sliding three-blade plate A (332) is arranged on the inner wall of the U-shaped cylinder B (33), the length of the sliding three-blade plate A (332) is equal to the axial depth of the U-shaped cylinder B (33), and gaps B are reserved between the sliding three-blade plate A (332), the fixed three-blade plate A (321) and the threaded piston rod (13); the sliding three-bladed plate A (332) is in sliding contact with the fixed three-bladed plate A (321); the left end of the U-shaped cylinder B (33) is positioned outside the U-shaped cylinder A (32), and a plurality of throttling ports A (331) allowing damping fluid to flow are formed in the U-shaped cylinder B; a support A (36) is fixedly arranged at the left end of the U-shaped cylinder B (33); the inner wall of the U-shaped cylinder A (32) and the outer wall of the threaded piston rod (13) form a basic rotating cavity A (34), and the inner wall of the U-shaped cylinder B (33) and the outer wall of the threaded piston rod (13) form an extended rotating cavity A (35);
the planetary damping device comprises a planetary gear (41) which is meshed with the external thread of the threaded gear (31) and the internal thread of the threaded cylinder body (10) for transmission, a U-shaped cylinder C (42) with the right end fixedly connected with the planetary gear (41), and a U-shaped cylinder D (43) with the right end extending into the U-shaped cylinder C (42) and capable of sliding along the axial direction of the threaded piston rod (13); the inner wall of the U-shaped cylinder C (42) is in sliding contact with the outer wall of the U-shaped cylinder D (43); a fixed three-blade plate B (421) is arranged at the right end of the U-shaped cylinder C (42), a gap C for the U-shaped cylinder D (43) to pass through is reserved between the fixed three-blade plate B (421) and the inner wall of the U-shaped cylinder C (42), and the length of the fixed three-blade plate B (421) is equal to the axial depth of the U-shaped cylinder C (42); the inner wall of the U-shaped cylinder D (43) is provided with a sliding three-blade plate B (432), and the length of the sliding three-blade plate B (432) is equal to the axial depth of the U-shaped cylinder D (43); the sliding three-leaf plate B (432) is in sliding contact with the fixed three-leaf plate B (421); the left end of the U-shaped cylinder D (43) is positioned outside the U-shaped cylinder C (42), and a plurality of throttling ports B (431) allowing damping fluid to flow are formed in the U-shaped cylinder D; the left end of the U-shaped cylinder D (43) is rotatably provided with a support column B (46); the inner cavity of the U-shaped cylinder C (42) is a basic rotating cavity B (44), and an expanded rotating cavity B (45) is arranged in the U-shaped cylinder D (43);
the gear axial positioning device comprises a support plate (21) fixedly arranged in the threaded cylinder body (10), a hollow sleeve (26) with the left end fixedly arranged on the right end surface of the threaded gear (31) and the right end penetrating through the support plate (21) and rotatably arranged on the support plate (21), a thrust plate A (22) and a thrust plate B (23) fixedly arranged on the hollow sleeve (26) and respectively positioned on the left side and the right side of the support plate (21), a thrust bearing A (24) arranged between the thrust plate A (22) and the support plate (21), and a thrust bearing B (25) arranged between the support plate (21) and the thrust plate B (23);
a cross frame rod (5) is further arranged in the threaded cylinder body (10), the left end of the strut A (36) is fixedly arranged in the middle of the cross frame rod (5), and the left end of the strut B (46) is fixedly arranged at the branch end of the cross frame rod (5);
a liquid cavity (14) filled with damping liquid is formed between the end cover A (11) and the support plate (21) inside the threaded cylinder body (10), and the damping liquid in the liquid cavity (14) can flow left and right through the throttling opening A (331) and the throttling opening B (431).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110669890.5A CN113294478B (en) | 2021-06-17 | 2021-06-17 | Damping force is directly proportional to liquid damper of displacement |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110669890.5A CN113294478B (en) | 2021-06-17 | 2021-06-17 | Damping force is directly proportional to liquid damper of displacement |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113294478A CN113294478A (en) | 2021-08-24 |
| CN113294478B true CN113294478B (en) | 2022-04-22 |
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| CN113685476B (en) * | 2021-08-30 | 2022-09-23 | 常州大学 | Liquid damper with damping force jumping along with displacement |
| CN114293673B (en) * | 2021-12-20 | 2023-06-06 | 长安大学 | Multidirectional vibration damping energy consumption device |
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| US6260832B1 (en) * | 1997-12-17 | 2001-07-17 | Marzocchi S.P.A. | Shock absorber with adjustable compression and rebound |
| CN1811219A (en) * | 2005-01-25 | 2006-08-02 | 王宝国 | Hydraulic bidirection return stroke damper |
| CN105042018A (en) * | 2015-06-30 | 2015-11-11 | 南平市建阳区汽车锻压件厂 | Hydraulic drive friction locking direct connection type differential mechanism with damping structures |
| CN108105316A (en) * | 2017-12-15 | 2018-06-01 | 常州大学 | A kind of damping modulator based on fluid velocity decomposition |
| CN111623074A (en) * | 2020-05-27 | 2020-09-04 | 常州大学 | Fluid-excited fluid-solid mixed damper |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6260832B1 (en) * | 1997-12-17 | 2001-07-17 | Marzocchi S.P.A. | Shock absorber with adjustable compression and rebound |
| CN1811219A (en) * | 2005-01-25 | 2006-08-02 | 王宝国 | Hydraulic bidirection return stroke damper |
| CN105042018A (en) * | 2015-06-30 | 2015-11-11 | 南平市建阳区汽车锻压件厂 | Hydraulic drive friction locking direct connection type differential mechanism with damping structures |
| CN108105316A (en) * | 2017-12-15 | 2018-06-01 | 常州大学 | A kind of damping modulator based on fluid velocity decomposition |
| CN111623074A (en) * | 2020-05-27 | 2020-09-04 | 常州大学 | Fluid-excited fluid-solid mixed damper |
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