CN109083967B - Spiral gas inerter - Google Patents

Spiral gas inerter Download PDF

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CN109083967B
CN109083967B CN201811010183.XA CN201811010183A CN109083967B CN 109083967 B CN109083967 B CN 109083967B CN 201811010183 A CN201811010183 A CN 201811010183A CN 109083967 B CN109083967 B CN 109083967B
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cylinder
spiral
piston
piston rod
inerter
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CN109083967A (en
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陈志强
张海中
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Nanjing University of Science and Technology
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Nanjing University of Science and Technology
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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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1034—Vibration-dampers; Shock-absorbers using inertia effect of movement of a liquid
    • 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
    • F16F9/18—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 with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/20—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 with a closed cylinder and a piston separating two or more working spaces therein with the piston-rod extending through both ends of the cylinder, e.g. constant-volume dampers
    • 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
    • F16F9/3207—Constructional features

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention discloses a spiral gas inerter, which comprises a cylindrical tank body, a spiral pipeline, a piston rod, a baffle plate and a horizontal baffle plate, wherein the horizontal baffle plate is arranged in the cylindrical tank body, the horizontal baffle plate divides the cylindrical tank body into an upper cavity and a lower cavity which are not communicated independently, the upper cavity is a cylinder, the lower cavity is a stroke chamber, the piston is fixed on the piston rod, the baffle plate is fixed on the bottom surface of the piston rod, the center of the baffle plate is provided with a round hole, the piston rod is arranged in the cylindrical tank body and penetrates through the round hole, the upper end of the piston rod extends out of the center of the top surface of the cylinder, so that the piston is positioned in the cylinder, the baffle plate is positioned in. The piston moves in the cylinder, the movement stroke of the piston is between two pipe orifices of the spiral pipeline, a section of liquid is filled in the spiral pipeline, and the liquid can only flow back and forth in the spiral pipeline 3 and can not enter the cylinder.

Description

Spiral gas inerter
Technical Field
The invention belongs to an energy storage element, and particularly relates to a spiral gas inerter.
Background
In the second type of electromechanical analogy theory, the force and current, the velocity and voltage, the mass element and the capacitance element, the damping element and the resistance element, and the spring element and the inductance element are similar to each other, however, according to the definition of newton's second motion law, the mass element must be referenced to the inertial coordinate system, and the acceleration is the absolute acceleration. Thus, the mass element is a single end point element (the other end point being the earth center) as distinguished from the spring element and the damping element. The capacitance element which is similar to the mass element in electromechanics needs to be grounded, so that an asymmetric relationship is formed, the mechanical vibration network and the circuit network cannot be completely similar, and the research and the application of the electromechanics similarity theory are hindered.
To address the deficiencies of this theory, professor Malcolm c. smith, cambridge university, england, first proposed the concept of inerter, and called an inerter with this dynamic characteristic. On the basis of the concept of the inertial capacitance, in the second electromechanical similarity theory, the corresponding relationship between the mass element and the grounding capacitance element is changed into the corresponding relationship between the inertial capacitance element and the common capacitance element, and the corresponding relationship promotes the development of the electromechanical similarity theory.
Inerter is a two-terminal mechanical element with the characteristic that when a pair of forces acts on two terminals, the force is proportional to the relative acceleration between the two terminals, the ratio being called the inertia of the inerter. The inerter serves as a passive mechanical element, and compared with a mass block, the inerter, a spring and a damper can form a richer passive mechanical structure. At present, the inertial volume is applied to the fields of formula one racing, house vibration reduction and the like.
At present, the realization forms of the inerter mainly comprise a gear and rack type inerter, a ball screw type inerter, a torsion type inerter, a hydraulic piston type inerter, a hydraulic pump type inerter and a spiral liquid inerter.
S.J. swift and Malcolm C.Smith et al in "Design and modeling of a fluidierter" have proposed that spiral liquid is used to hold, and this spiral liquid is used to hold and is formed by cylindrical pneumatic cylinder, spiral pipeline, piston rod, and the piston is fixed on the piston rod, and the piston rod upper end stretches out the pneumatic cylinder top surface center for the piston is located the pneumatic cylinder, and the spiral pipeline is the spiral winding at the pneumatic cylinder outer wall, and two ports of spiral pipeline are linked together with the pneumatic cylinder. One nozzle of the spiral pipeline is positioned above the other nozzle, and the piston moves in the hydraulic cylinder, and the moving stroke of the piston is between the two nozzles. The spiral pipeline and the hydraulic cylinder are filled with liquid. When the force F acts on any one end point (the top of the piston rod is provided with an end point, and the center of the bottom surface of the cylindrical hydraulic cylinder is provided with an end point), the two end points move relatively, so that the piston pushes the liquid in the hydraulic cylinder to move, the liquid enters the spiral pipeline, and the liquid in the spiral pipeline is pushed to do spiral motion in the spiral pipeline.
The defects of the spiral liquid inerter mainly comprise:
(1) the liquid in the spiral pipe is subjected to a large resistance.
(2) The liquid in the hydraulic cylinder has viscous friction with the wall of the hydraulic cylinder.
(3) The spiral pipe and the hydraulic cylinder are connected to lose kinetic energy.
(4) The work done by the force F cannot be converted into the kinetic energy of the movement of the liquid in the spiral pipe, and a part of the work is converted into the kinetic energy of the liquid in the hydraulic cylinder.
These disadvantages result in a higher degree of non-linearity of the helical liquid inertance, and are not suitable for the situation where the requirement on the degree of linearity of the inertance is higher.
Disclosure of Invention
The invention aims to provide a spiral gas inerter, which overcomes the defects of the spiral liquid inerter, reduces the non-linear degree of the inerter and is more suitable for the situation with higher requirement on the linear degree of the inerter.
The technical solution for realizing the purpose of the invention is as follows: the utility model provides a spiral gaseous being used to and holding, including cylindrical jar body, helical pipeline, piston rod, baffle and horizontal baffle, cylindrical jar internal horizontal baffle that is equipped with, two upper and lower independent cavities that do not communicate are cut apart into with cylindrical jar body to horizontal baffle, the cavity that is located the top is the cylinder, the cavity that is located the below is the stroke room, the piston is fixed on the piston rod, the baffle is fixed in the piston rod bottom surface, the baffle center is equipped with the round hole, the piston rod sets up at cylindrical jar internal and passes the round hole, and stretch out cylinder top surface center on the piston rod, make the piston be located the cylinder, the baffle is located the stroke room, helical pipeline is spiral winding at cylindrical jar external wall, two ports.
The piston moves in the cylinder, the movement stroke of the piston is between two pipe orifices of the spiral pipeline, a section of liquid is filled in the spiral pipeline, and the liquid can only flow back and forth in the spiral pipeline and can not enter the cylinder.
Compared with the prior art, the invention has the remarkable advantages that:
(1) the liquid in the spiral pipeline has only one section, and the length of the section is smaller than that of the spiral pipeline, so that the viscous effect of the liquid in the spiral pipeline is smaller.
(2) The friction between the gas in the cylinder and the cylinder wall is negligible and is much smaller than the viscous effect of the liquid in the cylinder.
(3) The liquid in the spiral pipeline does not enter the cylinder, so the kinetic energy loss at the joint of the spiral pipeline and the hydraulic cylinder is avoided;
(4) the cylinder is not filled with liquid, and if other losses are neglected, the work of the force F is completely converted into the kinetic energy of the liquid in the spiral pipeline in spiral motion.
Drawings
FIG. 1 is a schematic diagram of the overall structure of the present invention.
Fig. 2 is a cross-sectional view of the present invention.
Detailed Description
The present invention is described in further detail below with reference to the attached drawing figures.
With reference to fig. 1 and 2, the spiral gas inerter comprises a cylindrical tank body, a spiral pipeline 3, a piston 5, a piston rod 6, a baffle 7 and a horizontal baffle 9, wherein the cylindrical tank body is internally provided with the horizontal baffle 9, the horizontal baffle 9 divides the cylindrical tank body into an upper cavity and a lower cavity which are not communicated independently, the upper cavity is a cylinder 4, the lower cavity is a stroke chamber 8, the piston 5 is fixed on the piston rod 6, the baffle 7 is fixed on the bottom surface of the piston rod 6, the center of the baffle 7 is provided with a circular hole, the piston rod 6 is arranged in the cylindrical tank body and penetrates through the circular hole, the upper end of the piston rod 6 extends out of the center of the top surface of the cylinder 4, so that the piston 5 is positioned in the cylinder 4, the baffle 7 is positioned in the stroke chamber 8, the spiral pipeline 3 is spirally wound on the outer.
One orifice of the spiral pipeline 3 is positioned above the other orifice, and the piston 5 moves in the cylinder 4 with the moving stroke between the two orifices. The spiral pipe 3 contains a section of liquid which can only flow back and forth in the spiral pipe 3 and cannot enter the cylinder 4.
When the inerter works, the movement stroke of the baffle 7 in the stroke chamber 8 limits the movement stroke of the piston 5 in the cylinder 4, so that liquid in the spiral pipeline 3 is prevented from entering the cylinder 4 to prevent the inerter from working normally.
And the piston rod 6 is tightly matched with the top surface of the cylinder 4 and the piston rod 6 is tightly matched with the baffle 7, and sealing is realized through a sealing ring.
The working principle of the spiral gas inerter is as follows: when the force F acts on any end point (the top of the piston rod 6 is provided with a first end point 1, and the center of the bottom surface of the cylindrical tank body is provided with a second end point 2), the first end point 1 and the second end point 2 move relatively, so that the piston 5 pushes the gas in the cylinder 4 to move, the gas enters the spiral pipeline 3, and a section of liquid in the spiral pipeline 3 is pushed to make spiral motion in the spiral pipeline 3. Setting a section of liquid in the spiral pipe 3The density of the body is rho, the length is l, the radius of the piston 5 is R, the radius of the cross section of the piston rod 6 is R, and the sectional area of the liquid in the spiral pipeline 3 is A2The relative displacement of the first end point 1 and the second end point 2 is x and the velocity of the liquid in the helical conduit 3 is u. The effective working area of the piston 5 is a1＝π(R2-r2) The relative speed of the first endpoint 1 and the second endpoint 2 is
Figure BDA0001784851660000046
The flow of the cross section of the liquid in the spiral duct 3 is equal to the flow of the cross section of the cylinder, so
Figure BDA0001784851660000041
Figure BDA0001784851660000042
If the gravity work and various losses of the liquid in the spiral pipeline 3 are neglected, the work of the force F is converted into the kinetic energy of the liquid in the spiral pipeline 3 in the spiral motion, and the power of the force F is equal to the time change rate of the kinetic energy of the liquid in the spiral pipeline 3 in the spiral motion, namely
Figure BDA0001784851660000043
Can obtain the product
Figure BDA0001784851660000044
The above equation indicates the relative acceleration between the force F and the first endpoint 1 and the second endpoint 2
Figure BDA0001784851660000047
The spiral gas inerter is in direct proportion and meets the characteristic of inerter, so that the spiral gas inerter is really an implementation form of the inerter. Wherein the ratio of
Figure BDA0001784851660000045
Called the inertia of the helical gas inerter.
Compared with the traditional spiral liquid inerter, the spiral gas inerter has the advantages that:
(1) the liquid in the spiral pipeline 3 has only one section, and the length of the section is less than that of the spiral pipeline 3, so the viscous effect of the liquid in the spiral pipeline 3 is smaller.
(2) The friction between the gas in the cylinder 4 and the cylinder wall is negligible and much less than the viscous effect of the liquid in the cylinder.
(3) The liquid in the spiral pipe 3 does not enter the cylinder 4, so the kinetic energy loss at the joint of the spiral pipe 3 and the hydraulic cylinder is avoided.
(4) No liquid is in the cylinder 4, and if other losses are neglected, the work of the force F is completely converted into the kinetic energy of the liquid in the spiral pipeline 3 in spiral motion.
The advantages enable the nonlinear degree of the spiral gas inerter to be far lower than that of the spiral liquid inerter, and the method is more suitable for the situation with higher requirement on the linear degree of the inerter.
The spiral inertial container has the important characteristics that: when the spiral gas inerter is horizontally arranged and works in a horizontal state, if the liquid in the spiral pipeline 3 is in integral circles, the integral gravitational potential energy is unchanged when the liquid flows in the spiral pipeline 3, and the algebraic sum of the applied gravitational force is zero. From the calculation of inertia, it can be seen that the force F and the relative acceleration between the two end points
Figure BDA0001784851660000051
The function relationship of the spiral gas inerter is closer to a linear relationship, the linear degree of the spiral gas inerter is higher, and the spiral gas inerter can reach the linear degree index of the inerter compared with other existing implementation forms of the inerter.

Claims (2)

1. A spiral gas inerter is characterized in that: the spiral-flow type piston cylinder comprises a cylindrical cylinder body, a spiral pipeline (3), a piston (5), a piston rod (6), a baffle (7) and a horizontal baffle (9), wherein the horizontal baffle (9) is arranged in the cylindrical cylinder body, the horizontal baffle (9) divides the cylindrical cylinder body into an upper cavity and a lower cavity which are not communicated independently, the cavity positioned above is a cylinder (4), the cavity positioned below is a stroke chamber (8), the piston (5) is fixed on the piston rod (6), the baffle (7) is fixed on the bottom surface of the piston rod (6), a round hole is formed in the center of the baffle (7), the piston rod (6) is arranged in the cylindrical cylinder body and penetrates through the round hole, the upper end of the piston rod (6) extends out of the center of the top surface of the cylinder (4), so that the piston (5) is positioned on the cylinder (4), the baffle (7) is, two ports of the spiral pipeline (3) are communicated with the cylinder (4);
the piston (5) moves in the cylinder (4), the movement stroke of the piston is between two pipe orifices of the spiral pipeline (3), a section of liquid is filled in the spiral pipeline (3), and the liquid can only flow back and forth in the spiral pipeline (3) and cannot enter the cylinder (4).
2. The helical gas inerter of claim 1, wherein: and the piston rod (6) is tightly matched with the top surface of the air cylinder (4) and the piston rod (6) is tightly matched with the baffle plate (7), and sealing is realized through a sealing ring.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112594320B (en) * 2020-12-02 2022-06-21 江苏大学 Inertial volume and magnetorheological damping fusion type suspension vibration damping mechanism
CN114763817B (en) * 2021-01-14 2024-04-09 南京理工大学 Inertial container device with rod type structure
CN114033828B (en) * 2021-11-15 2023-07-14 广州大学 Novel hydraulic type inertial damping device

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3879023A (en) * 1973-12-13 1975-04-22 Dow Chemical Co Method for absorbing and releasing energy
CN101709760A (en) * 2009-12-21 2010-05-19 重庆工商大学 Variable inertial mass hydraulic damper
CN103059514A (en) * 2012-12-05 2013-04-24 哈尔滨工业大学 Preparation method of magnetic lyophoby type carbon nano tube base nanochannel damping plate and damper
CN103644248A (en) * 2013-12-13 2014-03-19 江苏大学 Inerter and damping controllable magneto-rheological inerter device and control method thereof
CN104553654A (en) * 2014-12-02 2015-04-29 江苏大学 Oil gas suspension system with inertia energy storage element
CN104763768A (en) * 2014-12-02 2015-07-08 江苏大学 Inert and damping integrated gas-filled damper
CN105508492A (en) * 2015-12-17 2016-04-20 江苏大学 Spring and damping inertial container integrated suspension

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3879023A (en) * 1973-12-13 1975-04-22 Dow Chemical Co Method for absorbing and releasing energy
CN101709760A (en) * 2009-12-21 2010-05-19 重庆工商大学 Variable inertial mass hydraulic damper
CN103059514A (en) * 2012-12-05 2013-04-24 哈尔滨工业大学 Preparation method of magnetic lyophoby type carbon nano tube base nanochannel damping plate and damper
CN103644248A (en) * 2013-12-13 2014-03-19 江苏大学 Inerter and damping controllable magneto-rheological inerter device and control method thereof
CN104553654A (en) * 2014-12-02 2015-04-29 江苏大学 Oil gas suspension system with inertia energy storage element
CN104763768A (en) * 2014-12-02 2015-07-08 江苏大学 Inert and damping integrated gas-filled damper
CN105508492A (en) * 2015-12-17 2016-04-20 江苏大学 Spring and damping inertial container integrated suspension

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