CN112963483A - Piston cylinder oil cavity damper - Google Patents

Piston cylinder oil cavity damper Download PDF

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Publication number
CN112963483A
CN112963483A CN202110326277.3A CN202110326277A CN112963483A CN 112963483 A CN112963483 A CN 112963483A CN 202110326277 A CN202110326277 A CN 202110326277A CN 112963483 A CN112963483 A CN 112963483A
Authority
CN
China
Prior art keywords
compensation
oil hole
oil
valve port
piston valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202110326277.3A
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Chinese (zh)
Inventor
孙凤
曲帅
赵海宁
单光坤
徐方超
***
金俊杰
郭辉
张晓友
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Shenyang University of Technology
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Shenyang University of Technology
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Publication date
Application filed by Shenyang University of Technology filed Critical Shenyang University of Technology
Priority to CN202110326277.3A priority Critical patent/CN112963483A/en
Publication of CN112963483A publication Critical patent/CN112963483A/en
Pending legal-status Critical Current

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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
    • 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
    • F16F9/185—Bitubular units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
    • B60G17/08—Characteristics of fluid 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
    • F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
    • 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
    • F16F15/022—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 dampers and springs in combination
    • 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
    • F16F15/023—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 fluid means
    • 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
    • F16F15/03—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 magnetic or electromagnetic means
    • 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
    • F16F15/046—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 using combinations of springs of different kinds
    • 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
    • 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
    • F16F9/3235—Constructional features of cylinders
    • 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
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3482—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body the annular discs being incorporated within the valve or piston body
    • 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
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F16F9/5126—Piston, or piston-like valve elements
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/06—Magnetic or electromagnetic
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/12—Fluid damping
    • 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
    • F16F2238/00—Type of springs or dampers
    • F16F2238/02—Springs
    • F16F2238/026—Springs wound- or coil-like

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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)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention relates to a piston cylinder oil cavity damper which comprises a hollow oil cavity, an upper piston head valve, a lower oil cavity and a compensation cavity. The oil-gas-liquid-type compensation device is provided with an upper oil cavity, a lower oil cavity and a compensation cavity, wherein each oil cavity is subjected to oil liquid replacement through a piston valve port, a piston head connected with the lower end of a piston cylinder is used for oil liquid replacement, a secondary rod (the piston cylinder) integrally moves in the lower oil cavity, the lower oil cavity is a hollow cylinder, a lower-end piston valve is matched below the cylinder, and the lower-end piston valve is seated in a circular sink groove 5-1 machined in the bottom of the compensation cavity. The invention aims to provide an improved damper for an oil chamber of a piston cylinder, which can be matched with an electromagnetic active suspension. The intention is to make reasonable use of the structure of the damper to optimize the space of the electromagnetic active suspension and the like; in addition, the supporting rigidity is high, the bending moment resistance is high, and the installation space is reduced; in addition, the inner space of the damper piston cylinder is used as an upper oil cavity, so that the structure is optimized.

Description

Piston cylinder oil cavity damper
Technical Field
The invention relates to a design of an oil cavity damper of a piston cylinder of an active suspension, belonging to the technical field of automobile suspension systems.
Background
At present, domestic vehicle suspensions are mainly passive suspensions, are simple in structure and low in cost and are widely applied, but damping and natural frequency of the suspensions are not adjustable, and different road conditions can only be met according to parameters after delivery from factories; along with the continuous improvement of the living standard of people, the requirements of people on the riding comfort and the operation stability of automobiles are higher and higher, therefore, an active suspension with adjustable parameters is produced, the active suspension can sense the vibration transmitted to wheels from different road conditions according to sensors, carry out signal feedback, and then actively adjust the suspension parameters to deal with different road conditions, but the existing active suspension usually replaces part of the structure of the original suspension or completely abandons the original structure, so that the connection mode of the designed active suspension to the original suspension and an automobile body is changed, the suspension is not only required to be designed, but also other mechanisms connected with the suspension are required to be designed, the changed assembly becomes more complex, the size of the suspension is larger, the required design cost is higher, the original vehicle suspension cannot be directly replaced, and the existing active suspension only has research value, cannot be widely applied in a short time.
Disclosure of Invention
The purpose of the invention is as follows:
the technical problem to be solved by the invention is as follows: the problems of the permanent magnet assembly position and the space occupied by the electromagnetic suspension encountered in the design process of the electromagnetic active suspension.
The technical scheme is as follows:
a piston cylinder oil chamber damper comprises a piston cylinder (1) with a hollow interior, a cavity shell (23) and an upper end piston valve (3) arranged in the cavity shell (23);
one end opening of the piston cylinder (1) is closed, the other end opening of the piston cylinder is used as a valve port and extends into the cavity shell (23) to be connected with the upper end piston valve (3), the piston cylinder (1) is of a structure which can do telescopic reciprocating motion relative to the cavity shell (23) so as to drive the upper end piston valve (3) to axially move along the cavity shell (23), and the outer side wall of the piston cylinder (1) is in dynamic sealing fit with the inner side wall of the cavity shell (23);
the interior of the piston cylinder (1) is hollow and serves as an upper oil cavity (1-1), and the part inside the cavity shell (23) and below the upper end piston valve (3) is a lower oil cavity (4);
an upper valve piston valve port is arranged on the upper end piston valve (3), and oil displacement is carried out on the upper oil cavity and the lower oil cavity (4) through the upper valve piston valve port;
a compensation cavity (5) is arranged below the lower oil cavity (4) or on the periphery of the side wall;
a lower end piston valve (6) is arranged between the lower oil cavity (4) and the compensation cavity (5), a lower valve piston valve port is arranged on the lower end piston valve (6), and oil is replaced between the lower oil cavity (4) and the compensation cavity (5) through the lower valve piston valve port.
The upper end piston valve (3) comprises a piston valve port plate (9) and an upper valve piston valve port arranged on the piston valve port plate (9), and the upper valve piston valve port comprises an upper oil hole (22) and a lower oil hole (21);
the upper oil hole (22) and the lower oil hole (21) are arranged in a staggered manner, a piston valve port upper pressure plate (11) is arranged above the upper oil hole (22), and the piston valve port upper pressure plate (11) is of a structure which can cover the upper oil hole (22) when in use and can be jacked open under the jacking force of oil in the lower oil cavity (4) to open the upper oil hole (22);
a piston valve port lower pressing sheet (13) is arranged below the lower oil hole (21), and the piston valve port lower pressing sheet (13) is a structure which can cover the lower oil hole (21) when in use and can be jacked under the pressure of oil in an upper oil cavity so that the lower oil hole (21) is opened.
The lower piston valve (6) comprises a lower piston valve port plate (15) and a lower valve piston valve port arranged on the lower piston valve port plate (15), and the lower valve piston valve port comprises a lower compensation oil hole (16) and an upper compensation oil hole (18);
the lower compensation oil hole (16) and the upper compensation oil hole (18) are arranged in a staggered manner, an upper compensation oil hole pressing sheet (14) is arranged above the upper compensation oil hole (18), and the upper compensation oil hole pressing sheet (14) is of a structure which can cover the upper compensation oil hole (18) when in use and can be jacked open under the action of the oil jacking force in the compensation cavity (5) so that the upper compensation oil hole (18) is opened;
and a compensation lower oil hole pressing sheet (19) is arranged below the compensation lower oil hole (16), and the compensation lower oil hole pressing sheet (19) is a structure which can cover the compensation lower oil hole (16) when in use and can be jacked open under the action of the oil pressure of the lower oil cavity (4) so that the compensation lower oil hole (16) is opened.
The lower oil hole (21) is arranged around the upper oil hole (22);
the compensation upper oil hole (18) is arranged around the compensation lower oil hole (16).
An upper valve port pressing sheet connecting bolt (12) is arranged in the center of the piston valve port plate (9), a piston valve port upper pressing plate (11) and a piston valve port lower pressing plate (13) are arranged on the connecting bolt (12), the piston valve port upper pressing plate (11) can cover the area where the upper oil hole (22) is located, the piston valve port lower pressing plate (13) can cover the area where the lower oil hole (21) is located, and a hole (A) is reserved in the area corresponding to the upper oil hole (22);
the center of the lower piston valve plate (15) is provided with a lower valve port pressing sheet connecting bolt (17), the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are sleeved on the lower valve port pressing sheet connecting bolt (17), the compensation lower oil hole pressing sheet (19) can cover the region where the compensation lower oil hole (16) is located, the compensation upper oil hole pressing sheet (14) can cover the region where the compensation upper oil hole (18) is located, and a hole is reserved in the region corresponding to the compensation lower oil hole (16).
The piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13) are non-elastic plates or elastic plates;
when the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) are non-elastic plates: the piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13) are structures which can move along the upper valve port pressing plate connecting bolt (12) to control the opening and closing of the upper oil hole (22) and the lower oil hole (21);
when piston valve port top board (11) and piston valve port holding down board (13) are the elastic plate: the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) directly cover the upper oil hole (22) and the lower oil hole (21), and when the piston valve port upper pressing plate (11) or the piston valve port lower pressing plate (13) is impacted by oil, elastic deformation is generated to open the upper oil hole (22) or the lower oil hole (21).
The compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are non-elastic plates or elastic plates;
when the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are non-elastic plates: the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are structures which can move along the lower valve port pressing sheet connecting bolt (17) to control the opening and closing of the compensation upper oil hole (18) and the compensation lower oil hole (16);
when the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are elastic plates: the upper compensation oil hole pressing sheet (14) and the lower compensation oil hole pressing sheet (19) directly cover the upper compensation oil hole (18) and the lower compensation oil hole (16), and when the upper compensation oil hole pressing sheet (14) or the lower compensation oil hole pressing sheet (19) is impacted by oil, elastic deformation can be generated to open the upper compensation oil hole (18) or the lower compensation oil hole (16).
When the compensation cavity (5) is arranged on the periphery of the side wall of the lower oil cavity (4), a transition cavity (15-1) is formed at the bottom of the lower piston valve port plate (15), and the transition cavity (15-1) is communicated with the compensation cavity (5) through a channel (15-2) of the side wall.
A spiral spring (24) is sleeved outside the part, exposed out of the cavity shell (23), of the piston cylinder (1), the upper end of the spiral spring (24) is connected with an upper spring supporting seat (25), the lower end of the spiral spring (24) is connected with a lower spring supporting seat (26), a plurality of permanent magnets (2) are arranged on the outer wall of the piston cylinder (1), and a magnetic conduction ring (28) is arranged between every two adjacent permanent magnets (2); the two adjacent permanent magnets (2) are arranged in a way of opposite polarity;
the piston cylinder (1), the permanent magnet (2) and the magnetic conduction ring (28) form a secondary assembly, the secondary assembly penetrates through the primary assembly and can perform telescopic action relative to the primary assembly, the primary assembly comprises a primary outer cylinder (27), a primary winding (29) and a primary iron core (30), and the primary winding (29) and the primary iron core (30) are arranged in the primary outer cylinder (27) and are alternately arranged along the axial direction of the primary outer cylinder (27); the secondary assembly passes through the primary winding (29) and the primary iron core (30) and can do axial reciprocating movement relative to the primary winding (29) and the primary iron core (30).
A buffer block (31) is further arranged in the spiral spring (24), and the buffer block (31) is arranged between the spring upper supporting seat (25) and the primary outer cylinder (27).
The advantages and effects are as follows:
based on the traditional piston cylinder, the invention designs a novel damper piston cylinder which can be used as an upper oil cavity of a damper and can be assembled with a permanent magnet;
the piston cylinder is hollow as an upper oil cavity, and damping fluid is filled in the piston cylinder and can flow freely; the outer wall of the piston cylinder is used for matching the position of the electromagnetic suspension frame for assembling the permanent magnets in specific arrangement; wherein the piston cylinder can reciprocate in the damper. The piston head is connected with the lower end of the piston cylinder, the piston head is provided with a valve port, an oil outlet and an oil inlet with novel design are arranged on the piston head, an upper circular elastic sheet and a lower circular elastic sheet are fixed through bolts, and the coverage area of the upper circular elastic sheet and the lower circular elastic sheet corresponds to the position of the corresponding valve port (for example, an upper pressure plate 11 of the piston valve port is smaller than a lower pressure plate 13 of the piston valve port, the circle centers of the upper pressure plate and the lower pressure plate are coaxial, 11 corresponds. The damping liquid can flow freely in the upper oil cavity and the lower oil cavity.
The damper also comprises a lower oil cavity and a compensation cavity, wherein the lower oil cavity is divided into two oil cavities, namely a main lower oil cavity, a main lower oil cavity and the compensation cavity; the lower end of the lower oil cavity of the main lower oil cavity is connected with a piston head, and the piston head ensures that damping fluid freely flows in the lower oil cavity of the main lower oil cavity and the compensation cavity; the compensation cavity is used for reducing the pressure of the damping fluid of the lower oil cavity of the main lower oil cavity.
In addition, a linear slide rail is arranged at an opening at the upper end of the cavity shell (23), the piston cylinder is matched with the linear slide rail, and the piston cylinder moves in the lower oil cavity of the damper through the linear slide rail.
In conclusion, the oil-gas dual-purpose oil chamber has an upper oil chamber, a lower oil chamber and a compensation chamber, wherein each oil chamber is subjected to oil liquid replacement through a piston valve port, a piston head connected with the lower end of a piston cylinder is used for oil liquid replacement, a secondary rod (the piston cylinder) integrally moves in the lower oil chamber, the lower oil chamber is a hollow cylinder, a lower end piston valve is matched below the cylinder, and the cylinder is seated in a circular sink groove 5-1 machined in the bottom of the compensation chamber. The invention aims to provide an improved damper for an oil chamber of a piston cylinder, which can be matched with an electromagnetic active suspension. The intention is to make reasonable use of the structure of the damper to optimize the space of the electromagnetic active suspension and the like; in addition, the supporting rigidity is high, the bending moment resistance is high, and the installation space is reduced; in addition, the inner space of the damper piston cylinder is used as an upper oil cavity, so that the structure is optimized.
Drawings
FIG. 1 is a front sectional view of a piston barrel oil chamber damper of the present invention;
FIG. 2 is a schematic view of the upper piston valve port of the present invention;
FIG. 3 is a schematic view of the lower end piston valve port of the present invention;
FIG. 4 is a view of the valve port of the piston head of the present invention;
FIG. 5 is an exploded view of the components of FIG. 2 in connection;
FIG. 6 is a schematic structural diagram of the present invention applied to an electromagnetic active suspension;
FIG. 7 is a wiring diagram of the primary winding of the present invention;
fig. 8 is a schematic view of the primary core structure of the present invention;
FIG. 9 is a schematic diagram of a secondary assembly (piston cylinder) of the present invention in an elevational, cross-sectional, vertical arrangement
The names of the reference numbers in the figures are as follows:
1-piston cylinder (secondary rod); 2-permanent magnets in a specific arrangement; 3-upper piston valve; 4-a lower oil cavity; 5-a compensation cavity; 6-lower end piston valve; 7-an upper piston head; 8-sealing ring; 9-piston valve orifice plate; 10-fixing the bolt; 11-pressing the piston valve port; 12-upper valve opening pressing sheet connecting bolt; 13-pressing the lower part of the piston valve port; 14-compensation upper oil hole tabletting; 15-lower piston valve orifice plate; 16-offset down hole oil; 17-lower valve port pressing sheet connecting bolt; 18-compensation oil feeding hole; 19-compensation lower hole oil tabletting; 20-piston valve port; 21-a lower oil port; 22-oil feeding port;
24-a coil spring; 25-a spring upper support; 26-a lower spring support seat; 27-a primary outer barrel; 28-magnetic conductive ring; 29-a primary winding; 30-a primary core; 31-a buffer block; 32-primary upper cover plate; 33-upper plug; 34-an upper spring seat pressure plate; 35-primary outer cylinder connecting bolt; 36-a sealing ring pressure plate; 37-compensation chamber outer wall connecting bolt; 38-suspension lower connecting plate; 40-a primary lower cover plate; 41-sealing ring; 2-1-linear slide rail.
Detailed Description
A piston cylinder oil chamber damper is characterized in that: the damper comprises a piston cylinder (1) with a hollow interior, a cavity shell (23) and an upper end piston valve (3) arranged in the cavity shell (23);
one end opening of the piston cylinder (1) is closed (the upper end is shown in figure 1), the other end opening (the lower end is shown in figure 1) is used as a valve port and extends into the cavity shell (23) to be connected with the upper end piston valve (3) (the part of the periphery of a piston valve port plate (9) in the upper end piston valve (3) which is connected with the piston cylinder (1) is hermetically connected), the piston cylinder (1) is of a structure which can do telescopic reciprocating motion relative to the cavity shell (23) (namely, as shown in figure 1, does axial motion relative to the cavity shell (23), namely, as shown in figure 1, the piston cylinder moves up and down and stretches) to further drive the upper end piston valve (3) to axially move along the cavity shell (23), and the outer side wall of the piston cylinder (1) is in dynamic sealing fit with the inner side wall of the cavity shell (23); (As one of the modes, as shown in figure 1 and 2, the upper end piston valve (3) is arranged at the bottom of the upper piston head 7 at the lower part of the piston cylinder (1), the side wall of the upper piston head 7 is provided with a sealing ring 8, and the dynamic sealing of the side wall of the upper piston head 7 and the inner side wall of the cavity shell (23) is completed)
The interior of the piston cylinder (1) is hollow and serves as an upper oil cavity (1-1), and the part inside the cavity shell (23) and below the upper end piston valve (3) is a lower oil cavity (4);
an upper valve piston valve port is arranged on the upper end piston valve (3), and oil displacement is carried out on the upper oil cavity and the lower oil cavity (4) through the upper valve piston valve port;
a compensation cavity (5) is arranged below the lower oil cavity (4) or on the periphery of the side wall (when the side wall is provided with the compensation cavity, the side wall of the cavity shell (23) is an inner wall and an outer wall, and a cavity between the inner wall and the outer wall is the compensation cavity (5));
a lower end piston valve (6) is arranged between the lower oil cavity (4) and the compensation cavity (5), a lower valve piston valve port is arranged on the lower end piston valve (6), and oil is replaced between the lower oil cavity (4) and the compensation cavity (5) through the lower valve piston valve port.
The upper end piston valve (3) comprises a piston valve port plate (9) and an upper valve piston valve port arranged on the piston valve port plate (9), and the upper valve piston valve port comprises an upper oil hole (22) and a lower oil hole (21);
the upper oil hole (22) and the lower oil hole (21) are arranged in a staggered manner, a piston valve port upper pressure plate (11) is arranged above the upper oil hole (22), and the piston valve port upper pressure plate (11) is of a structure which can cover the upper oil hole (22) when in use and can be jacked open under the jacking force of oil in the lower oil cavity (4) to open the upper oil hole (22);
a piston valve port lower pressing sheet (13) is arranged below the lower oil hole (21), and the piston valve port lower pressing sheet (13) is a structure which can cover the lower oil hole (21) when in use and can be jacked under the pressure of oil in an upper oil cavity so that the lower oil hole (21) is opened.
The lower piston valve (6) comprises a lower piston valve port plate (15) and a lower valve piston valve port arranged on the lower piston valve port plate (15), and the lower valve piston valve port comprises a lower compensation oil hole (16) and an upper compensation oil hole (18);
the lower compensation oil hole (16) and the upper compensation oil hole (18) are arranged in a staggered manner, an upper compensation oil hole pressing sheet (14) is arranged above the upper compensation oil hole (18), and the upper compensation oil hole pressing sheet (14) is of a structure which can cover the upper compensation oil hole (18) when in use and can be jacked open under the action of the oil jacking force in the compensation cavity (5) so that the upper compensation oil hole (18) is opened;
and a compensation lower oil hole pressing sheet (19) is arranged below the compensation lower oil hole (16), and the compensation lower oil hole pressing sheet (19) is a structure which can cover the compensation lower oil hole (16) when in use and can be jacked open under the action of the oil pressure of the lower oil cavity (4) so that the compensation lower oil hole (16) is opened.
The lower oil hole (21) is arranged around the upper oil hole (22) (the upper oil hole (22) is arranged around the center of the piston valve plate (9), and the lower oil hole (21) is arranged around the upper oil hole (22) as shown in fig. 4);
the compensation upper oil hole (18) is arranged around the compensation lower oil hole (16) (the compensation lower oil hole (16) is arranged at the position, close to the center, of the lower piston valve port plate (15), and the compensation upper oil hole (18) is arranged on the periphery of the compensation lower oil hole (16) in the same way as the arrangement way of the lower oil hole (21) and the upper oil hole (22).
An upper valve port pressing sheet connecting bolt (12) is arranged in the center of the piston valve port plate (9), a piston valve port upper pressing plate (11) and a piston valve port lower pressing plate (13) are arranged on the connecting bolt (12), the piston valve port upper pressing plate (11) can cover the area where the upper oil hole (22) is located, the piston valve port lower pressing plate (13) can cover the area where the lower oil hole (21) is located, and a hole (A) is reserved in the area corresponding to the upper oil hole (22); (as shown in fig. 5, the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) are arranged on the connecting bolt (12), in order to prevent the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) from rotating, the connecting bolt (12) can be provided with a rotation stop key (12-1), of course, the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) do not have to rotate, because the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) can be both arranged in a circular shape, the covered and reserved area is not changed by rotating, because the upper oil holes (22) are arranged along the periphery of the connecting bolt (12), the area of the piston valve port upper pressing plate (11) only needs to be covered by the area, and because the lower oil holes (21) are arranged around the upper oil holes (22), the structure of the piston valve port lower pressing plate (13) is different from that of the piston valve port upper pressing plate (11), as shown in figure 5, a lantern ring (13-1) sleeved on a connecting bolt (12) is arranged in the middle of a piston valve port lower pressure plate (13), the lantern ring is connected with an outer plate (13-3) through a connecting rib (13-2), the connecting rib (13-2) avoids the area where an upper oil hole (22) is located, an area corresponding to the upper oil hole (22) is arranged between the lantern ring (13-1) and the outer plate (13-3), and the area is a reserved hole (A). That is, the position of the upper oil hole (22) is avoided at the aperture (A). Of course, other existing connection methods may be used, and are not described herein. )
The center of the lower piston valve plate (15) is provided with a lower valve port pressing sheet connecting bolt (17), the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are sleeved on the lower valve port pressing sheet connecting bolt (17), the compensation lower oil hole pressing sheet (19) can cover the region where the compensation lower oil hole (16) is located, the compensation upper oil hole pressing sheet (14) can cover the region where the compensation upper oil hole (18) is located, and a hole is reserved in the region corresponding to the compensation lower oil hole (16). (the setting relationship of the lower piston valve port plate (15), the lower valve port pressing sheet connecting bolt (17), the upper compensation oil hole pressing sheet (14) and the lower compensation oil hole pressing sheet (19) in the lower piston valve (6) is the same as the setting relationship of the piston valve port plate 9, the connecting bolt (12), the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) in the upper piston valve (3), which is not repeated here)
The piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13) are non-elastic plates or elastic plates;
when the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) are non-elastic plates: the piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13) are structures which can move (in parallel) along the upper valve port pressing plate connecting bolt (12) to control the opening and closing of the upper oil hole (22) and the lower oil hole (21); (the movement is not required to be overlarge, the movement distance between a piston valve port upper pressure plate (11) and a piston valve port lower pressure plate (13) is limited by a limit nut screwed on an upper valve port pressing plate connecting bolt (12), and an upper oil hole (22) and a lower oil hole (21) are controlled by the movement of the piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13))
When piston valve port top board (11) and piston valve port holding down board (13) are the elastic plate: the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) directly cover the upper oil hole (22) and the lower oil hole (21), and when the piston valve port upper pressing plate (11) or the piston valve port lower pressing plate (13) is impacted by oil, elastic deformation is generated to open the upper oil hole (22) or the lower oil hole (21). (without large displacement, the elastic deformation of the pressing sheet is depended on, the pressing sheet is similar to the pressing sheet squeezed open by oil, the pressing sheet is stressed to generate a certain amount of edge warping, the impact force disappears, and the automatic elastic reset is realized)
The compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are non-elastic plates or elastic plates;
when the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are non-elastic plates: the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are structures which can move (in parallel) along the lower valve port pressing sheet connecting bolt (17) to control the opening and closing of the compensation upper oil hole (18) and the compensation lower oil hole (16); (the movement is not required to be overlarge, the movement distance of the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) is limited by a limiting nut screwed on the lower valve port pressing sheet connecting bolt (17), and the compensation upper oil hole (18) and the compensation lower oil hole (16) are controlled to be opened and closed by the movement of the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19))
When the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are elastic plates: the upper compensation oil hole pressing sheet (14) and the lower compensation oil hole pressing sheet (19) directly cover the upper compensation oil hole (18) and the lower compensation oil hole (16), and when the upper compensation oil hole pressing sheet (14) or the lower compensation oil hole pressing sheet (19) is impacted by oil, elastic deformation can be generated to open the upper compensation oil hole (18) or the lower compensation oil hole (16) (no large displacement is generated, the elastic deformation of the pressing sheets is relied on, the pressing sheets are similar to the pressing sheets squeezed by the oil, a certain amount of edge warping is generated by the pressing sheets under stress, the impact force disappears, and automatic elastic reset is realized).
When the compensation cavity (5) is arranged on the periphery of the side wall of the lower oil cavity (4), a transition cavity (15-1) is formed at the bottom of the lower piston valve port plate (15), and the transition cavity (15-1) is communicated with the compensation cavity (5) through a channel (15-2) of the side wall.
A spiral spring (24) is sleeved outside the part, exposed out of the cavity shell (23), of the piston cylinder (1), the upper end of the spiral spring (24) is connected with an upper spring supporting seat (25), the lower end of the spiral spring (24) is connected with a lower spring supporting seat (26) (the lower spring supporting seat (26) is connected with the cavity shell (23) or the outer wall of the primary outer cylinder (27)), a plurality of permanent magnets (2) are arranged on the outer wall of the piston cylinder (1) (axially, namely from top to bottom as shown in figure 1), and a magnetic conduction ring (28) is arranged between every two adjacent permanent magnets (2); the two adjacent permanent magnets (2) are arranged in a way of opposite polarity;
the piston cylinder (1), the permanent magnet (2) and the magnetic conduction ring (28) form a secondary assembly, the secondary assembly penetrates through the primary assembly and can perform telescopic action relative to the primary assembly, (namely, the secondary assembly moves along the axial direction of the primary outer cylinder (27) as shown in figure 6) the primary assembly comprises a primary outer cylinder (27), a primary winding (29) and a primary iron core (30), the primary winding (29) and the primary iron core (30) are arranged in the primary outer cylinder (27), and the primary winding and the primary iron core are alternately arranged (namely, the primary winding and the primary iron core are alternately arranged one by one) along the axial direction (namely, the up-down direction as shown in figure 6) of the primary outer cylinder (27; the secondary assembly passes through the primary winding (29) and the primary iron core (30) and can reciprocate axially (i.e., up and down as shown in fig. 6) relative to the primary winding (29) and the primary iron core (30) (the bottom of the primary outer cylinder (27) is connected with the cavity shell (23)).
A buffer block (31) is further arranged in the spiral spring (24), and the buffer block (31) is arranged between the spring upper supporting seat (25) and the primary outer cylinder (27). The buffer block (31) is arranged at the bottom of the spring support seat (25) or at the top of the primary outer cylinder (27). The buffer block is used for preventing components such as a support seat (25) on a spring from impacting the primary outer cylinder (27) excessively when the lower movement amount of the secondary component is too large.
In summary, the damper assembly comprises an upper oil chamber and an upper piston valve 3 inside the piston cylinder 1, a lower oil chamber 4 and a lower piston valve 6 fitted therewith, and a compensation chamber 5. The hollow part of a piston is used as an upper oil cavity 1-1 of a damper, an upper end piston valve 3 is connected to a piston cylinder 1 through threads, the structural arrangement diagram is shown as figure 1, a sealing ring 8 is fixed on the outer side of the piston cylinder 1 (piston head) and is tightly attached to the inner wall of a lower oil cavity 4 of the damper, the piston cylinder 1 is connected with a piston valve port plate 9 through a fixing bolt 10, the shape of the piston valve port plate 9 is shown as figure 4, an upper oil hole 22 and a lower oil hole 21 are processed on a piston valve port sheet, and an upper piston valve port pressing sheet 11 and a lower piston valve port pressing sheet 13 are pressed through an upper valve port; when the piston cylinder 1 drives the upper piston valve 3 to move downwards, the lower pressing sheet 13 of the piston valve port tightly presses the lower oil hole 21 under the action of liquid pressure, and meanwhile, oil in the lower oil cavity pushes the upper pressing sheet 11 of the piston valve port to enter the upper oil cavity through the upper oil hole 22; when the piston cylinder 1 drives the upper piston valve 3 to move upwards, the pressure in the lower oil cavity becomes low, oil pushes the lower pressing sheet 13 of the piston valve port through the lower oil hole 21 and enters the lower oil cavity, at the same time, the upper pressing sheet 11 of the piston valve port is tightly pressed on the upper oil hole 22, a group of oil replacement of the upper oil cavity and the lower oil cavity is completed, the work of the upper oil cavity of the piston cylinder in figure 2 is completed, if the pressure of the lower oil cavity is too high, the oil cannot enter the upper oil cavity in time, at the same time, the lower oil cavity works, the structure of the lower oil cavity is the same as that of the upper piston valve plate, only the shape is different, when the pressure of the lower oil cavity is too high, part of the oil pushes the lower compensating oil hole pressing sheet 19 through the lower compensating oil hole 16 and enters the compensating cavity 5, at the upper compensating oil hole pressing sheet 19 tightly presses the upper compensating oil hole 36, when the pressure of the lower oil cavity is too low, part, at this time, the compensation lower oil hole pressing sheet 19 tightly presses the compensation lower oil hole 16, and the oil compensation is completed.
One embodiment is as follows:
fig. 6 is a schematic diagram of a vertical arrangement of a cylindrical linear motor type active suspension actuator according to the present invention, in a front view, in a cross section, the embodiment including: 33 upper plugs, 34 spring upper support seat pressing plates, 31 buffer blocks, 24 helical springs, 32 primary upper cover plates, 27 primary outer cylinders, 35 primary outer cylinder connecting bolts, 36 sealing ring pressing plates, 37 compensation cavity outer wall connecting bolts, 38 suspension lower connecting plates, 4 damper lower oil cavities, 25 spring upper support seats, 26 spring lower support seats, 40 primary lower cover plates, 41 sealing rings, 2-1 linear sliding rails and 5-compensation cavities.
The upper end of the upper plug 33 is provided with a hole which can be connected with an upper vehicle body, and the middle end and the lower end are provided with external threads which are used for connecting the spring upper supporting pressing plate 34 and the piston cylinder (secondary rod) 1. Support seat 25 and spring lower bearing 26 are the ring steel sheet on the spring, the shape forms through the punching press, support seat 25 is fixed with piston cylinder (secondary pole) 1 through support seat clamp plate 34 on the spring, spring lower bearing 26 passes through welded mode to be fixed on elementary urceolus 27, coil spring settles between upper and lower supporting seat, the elementary upper cover plate 32 of ring structure passes through welded fastening on elementary urceolus 27, the motion of secondary (piston cylinder (secondary pole) 1) assembly is guaranteed to the centre bore size. The primary lower cover plate 40 and the primary outer cylinder 27 are connected through a countersunk stud 35 to complete the packaging of the primary assembly, the sealing ring pressing plate 36 is a through-hole disc with a cylindrical boss shape, a linear guide rail 2-1 is arranged between the sealing ring pressing plate 36 and the primary lower cover plate 40 and used for supporting and guiding the up-and-down movement of the secondary assembly, the sealing ring pressing plate 36 is used for pressing a sealing ring 41 with a special structure to prevent oil in the compensation cavity 5 from leaking, the lower oil cavity 4 of the damper is of a through-core cylinder structure, the inner space is a movement space of the secondary assembly, the lower end of the cylinder is embedded into the lower piston head valve plate 15 and is seated in a circular countersunk groove 5-1 machined in the bottom of the cylinder in the compensation. The suspension lower connecting plate 38 is two rectangular steel plates, is connected with the wheel part through a processed circular through hole, and is fixed on the outer wall of the compensation cavity 4 in a welding mode. The compensation chamber is connected to the seal ring pressure plate 36 and the primary lower cover plate 40 by studs 37.
The primary assembly comprises a winding iron core assembly and a primary outer cylinder 27, the winding iron core assembly comprises a primary winding 29 and a primary iron core 30, the primary outer cylinder is of a through hole structure and is integrally sleeved outside the winding iron core assembly, a primary upper cover plate is connected with the primary outer cylinder through welding fixation to ensure that the upper end of the winding iron core assembly is fixed, a primary lower cover plate 40 is connected with the primary outer cylinder through a countersunk stud, the lower end position of the winding iron core assembly is fixed, and the primary assembly packaging is completed.
The primary iron core 30 in the winding iron core assembly is of a circular ring structure processed with square keys, the outer diameter of a circular ring is matched with the primary outer cylinder 27, the square keys are matched with key grooves of the primary outer cylinder 27 to ensure fixation, the inner diameter of the circular ring is slightly larger than the outer diameter of the secondary assembly to ensure the movement space of the secondary assembly (a piston cylinder (secondary rod) 1 with a permanent magnet and a magnetic conduction ring), the primary iron core 30 is in a shape of a circular cake, a bulge at the bottom in the figure 8 is a square key matched with the key grooves of the primary outer cylinder 27, the outer layer of the primary iron core 30 is coated with insulating paint to prevent conduction, a primary winding 29 is arranged between every two adjacent primary iron cores 30, the winding shape is a circular cake, coils are three-phase windings, the connection mode is shown in figure 7, each four groups are connected into one phase, the A1, the A2, the A3 and the A4 windings are in U phases, the B1, the B2, the B3 and the B4 are in V, The winding is characterized in that the windings of C2, C3 and C4 are W phases, U1, V1 and W1 are the head ends of the windings of each phase, U2, V2 and W2 are the tail ends of the windings of each phase, the tail ends of the windings of each phase are connected, three ports of U1, V1 and W1 are reserved, the three ports are connected with an external power supply, the windings are connected with three-phase alternating current, each group of coils is wrapped with a layer of polyimide film for insulation and coated with insulating heat-conducting silicone grease for heat conduction.
The secondary assembly is arranged in the primary assembly hole and comprises a piston cylinder (secondary rod) 1, permanent magnets 2 and magnetic conduction rings 28, as shown in fig. 9, the piston cylinder 1 is a cylinder with a through hole structure and made of non-magnetic steel, internal threads are processed at the upper end and the lower end and are respectively connected with an upper plug 33 and an upper piston head 7 at the upper end, the permanent magnets are in a circular ring shape and an axial magnetizing form, one magnetic conduction ring 28 is arranged between every two permanent magnets in a polar opposite arrangement mode, the magnetic conduction rings 28 are soft iron rings in a circular ring shape, the permanent magnets 2 and the magnetic conduction rings 28 are sleeved on the piston cylinder 1, the upper end is fixed by the upper plug 33, and the lower end is fixed by the upper piston head 7, so that the installation of the secondary assembly is completed. By utilizing the principle of electromagnetic induction, the magnetic field of the permanent magnet arranged on the piston cylinder 1 interacts with the magnetic field generated by electrifying the primary winding 29 in the primary assembly to output electromagnetic thrust.
The damper assembly comprises an upper oil chamber 1-1 and an upper piston head 7 inside a piston cylinder 1, a lower oil chamber 4 and a lower piston valve 6 matched with the lower oil chamber, and a compensation chamber 5. The hollow part of a piston cylinder 1 is used as an upper oil cavity 1-1 of a damper, an upper piston head 7 is connected to the piston cylinder 1 through threads, the structural arrangement drawings are shown as figures 1, 2 and 6, a sealing ring 8 is fixed on the outer side of the upper piston head 7 and is tightly attached to the inner wall of a lower oil cavity 4 of the damper, a piston valve port plate 9 is connected through a stud 10, the shape of the piston valve port plate 9 is shown as figure 4, an upper oil hole 22 and a lower oil hole 21 are processed on the piston valve port plate 9, an upper pressing sheet 11 of a piston valve port and a lower pressing sheet 13 of the piston valve port are pressed through a bolt 12, when the upper piston head 7 is driven by the piston cylinder 1 to move downwards, the lower pressing sheet 13 of the piston valve port tightly presses the lower oil hole 21 under the action of liquid pressure, and meanwhile; when the piston cylinder 1 drives the upper piston head 7 to move upwards, the pressure in the lower oil cavity becomes low, oil pushes the lower pressing piece 13 of the piston valve port through the lower oil hole 21 and enters the lower oil cavity, at the same time, the upper pressing piece 11 of the piston valve port is tightly pressed on the upper oil hole 22 to complete a group of oil replacement of the upper oil cavity and the lower oil cavity, if the pressure of the lower oil cavity is too high, the oil cannot enter the upper oil cavity in time and completely, at the same time, the lower piston works, the lower piston has the structure shown in figure 3, the structure principle is the same as that of the upper piston valve plate, only the shape is different, when the pressure of the lower oil cavity 4 is too high, part of the oil passes through the compensation lower oil hole 16, pushes the compensation lower pressing piece 19 of the compensation upper oil hole and enters the compensation cavity 5, at the compensation upper oil hole pressing piece 14 of the compensation upper oil hole tightly presses the compensation upper oil hole 18, when the pressure, at this time, the compensation lower oil hole pressing sheet 19 tightly presses the compensation lower oil hole 16, and the oil compensation is completed.
The assembly of the cylindrical linear motor type active suspension actuator of the embodiment during working is as follows: the upper end of the suspension is connected with the sprung mass, namely the weight of a vehicle body borne above the spring, by the upper plug 33 through the pin shaft hole, the secondary assembly is connected with the spring assembly, the spring assembly is connected with the primary assembly, the relation connection among the assemblies is guaranteed, the suspension is connected with the unsprung mass through the pin shaft hole of the suspension lower connecting plate 38, namely the wheel mass connected below the spring, and finally the integral installation is completed. That is, the cylindrical linear motor type active suspension actuator of the present embodiment is divided into a sprung mass and an unsprung mass, and is connected to the sprung mass through a pin shaft hole in the upper end of the piston cylinder in the secondary assembly, and is connected to the unsprung mass through a pin shaft hole in the lower connecting plate 38 of the compensation outdoor suspension.
The cylindrical linear motor type active suspension actuator is used as a cylindrical linear motor type active suspension actuator and has primary assembly and secondary assembly of specific structures, the primary assembly is assembly of a winding iron core, specifically a three-phase winding and a stator iron core, three-phase alternating current is introduced into the three-phase winding to generate a traveling wave magnetic field, meanwhile, the secondary assembly is a permanent magnet, a magnetic conduction ring and a piston cylinder, the annular permanent magnet adopts an axial magnetizing mode, the installation mode is N, S alternative arrangement, and the cylindrical linear motor type active suspension actuator has an extremely strong magnetic field, and generates electromagnetic thrust under the interaction of the primarily generated traveling wave magnetic field and the magnetic field of the magnet per se to drive the piston cylinder to perform reciprocating. Compared with the existing intermediate transmission device with hydraulic, gear rack and ball screw structures, the structure reduces transmission energy loss, has no rotational inertia and centrifugal force of a rotating motor, improves the response speed and control precision of the actuator, and has the advantages of high efficiency, stable operation, low noise, reliable work and the like. The embodiment integrates the traditional shock absorber and the cylindrical linear motor, saves the installation space, reduces the structural complexity, generates control force for active control, improves the performance of the suspension, has the Fail-Safe characteristic, ensures that the suspension can still normally work after the motor fails, and improves the operation stability and the running stability of the vehicle.
The working mode of the structure is as follows:
when the spiral spring 24 is compressed, oil in the upper oil cavity (1-1) and the lower oil cavity 4 is compressed by pressure, and when the relative movement speed is low, the pressure is not enough to open the valve port of the upper valve piston and the valve port of the lower valve piston, and oil exchange is not performed; when the relative speed is high, the pressure applied to the oil in the lower oil cavity 4 reaches a set maximum value at the moment, the buffering effect is limited, the valve port of the lower valve piston is opened, the oil in the lower oil cavity 4 is exchanged with the oil in the compensation cavity 5, and the buffering is performed by the damping force of the oil flowing through the valve port of the lower valve piston; after the buffering effect in the lower oil cavity 4 is limited, the valve port of the upper valve piston is opened to exchange oil in the upper oil cavity (1-1) and the lower oil cavity 4, and the oil flows through the damping force of the valve port of the upper valve piston to buffer; the cylindrical linear motor component formed by the primary assembly and the secondary assembly does not need to provide main power, but at the moment, the primary assembly and the secondary assembly still move relatively, and induced current can be generated by means of a magnetic field of the cylindrical linear motor component and can be stored and utilized.
Secondly, (when the suspension is impacted more greatly, the linear motor provides the main power) in this operating mode: when the relative speed is higher, the spiral spring 24 is compressed, and because the flow hysteresis of the oil in the upper oil cavity (1-1) and the lower oil cavity 4 is insufficient to rapidly provide damping force for effective buffering, the cylindrical linear motor assembly needs to be introduced with a certain value of current I (a specific value needs to be calculated by a controller of a vehicle according to actual impact conditions), and electromagnetic force is generated by means of a magnetic field, so that the main force I is provided, the compression speed is increased, the buffering capacity is improved, and induced current is not generated at the moment. After that, the helical spring 24 is greatly compressed, so that the expansion rebound can be accelerated, the damping force of oil exchange in the upper oil cavity (1-1) and the lower oil cavity 4 is not enough to control the rebound speed, at the moment, the cylindrical linear motor assembly needs to be introduced with a certain value of current II, and electromagnetic force is generated by depending on a magnetic field, so that a main power II is provided, and the rebound speed is controlled (the phenomenon that the rebound speed is too large and the vibration of a vehicle is too large is avoided).
Thirdly, (the suspension frame needs to provide larger supporting force under the working conditions of sharp turning, sharp acceleration and sharp braking, the linear motor provides main power): when the structure of the present application is not enough to support the coil spring 24 not to be compressed to provide an effective supporting force, a certain amount of current iii needs to be supplied to the cylindrical linear motor assembly, and an electromagnetic force is generated by a magnetic field, so as to provide a main force iii to provide an additional supporting force.
The above embodiment is only one form of application of the piston cylinder oil chamber damper of the present application to a cylinder linear motor type active suspension actuator, but may of course be applied in many other places where damping is required.

Claims (10)

1. A piston cylinder oil chamber damper is characterized in that: the damper comprises a piston cylinder (1) with a hollow interior, a cavity shell (23) and an upper end piston valve (3) arranged in the cavity shell (23);
one end opening of the piston cylinder (1) is closed, the other end opening of the piston cylinder is used as a valve port and extends into the cavity shell (23) to be connected with the upper end piston valve (3), the piston cylinder (1) is of a structure which can do telescopic reciprocating motion relative to the cavity shell (23) so as to drive the upper end piston valve (3) to axially move along the cavity shell (23), and the outer side wall of the piston cylinder (1) is in dynamic sealing fit with the inner side wall of the cavity shell (23);
the interior of the piston cylinder (1) is hollow and serves as an upper oil cavity (1-1), and the part inside the cavity shell (23) and below the upper end piston valve (3) is a lower oil cavity (4);
an upper valve piston valve port is arranged on the upper end piston valve (3), and oil displacement is carried out on the upper oil cavity and the lower oil cavity (4) through the upper valve piston valve port;
a compensation cavity (5) is arranged below the lower oil cavity (4) or on the periphery of the side wall;
a lower end piston valve (6) is arranged between the lower oil cavity (4) and the compensation cavity (5), a lower valve piston valve port is arranged on the lower end piston valve (6), and oil is replaced between the lower oil cavity (4) and the compensation cavity (5) through the lower valve piston valve port.
2. The piston cylinder oil chamber damper as claimed in claim 1, wherein: the upper end piston valve (3) comprises a piston valve port plate (9) and an upper valve piston valve port arranged on the piston valve port plate (9), and the upper valve piston valve port comprises an upper oil hole (22) and a lower oil hole (21);
the upper oil hole (22) and the lower oil hole (21) are arranged in a staggered manner, a piston valve port upper pressure plate (11) is arranged above the upper oil hole (22), and the piston valve port upper pressure plate (11) is of a structure which can cover the upper oil hole (22) when in use and can be jacked open under the jacking force of oil in the lower oil cavity (4) to open the upper oil hole (22);
a piston valve port lower pressing sheet (13) is arranged below the lower oil hole (21), and the piston valve port lower pressing sheet (13) is a structure which can cover the lower oil hole (21) when in use and can be jacked under the pressure of oil in an upper oil cavity so that the lower oil hole (21) is opened.
3. The piston cylinder oil chamber damper as claimed in claim 1, wherein: the lower piston valve (6) comprises a lower piston valve port plate (15) and a lower valve piston valve port arranged on the lower piston valve port plate (15), and the lower valve piston valve port comprises a lower compensation oil hole (16) and an upper compensation oil hole (18);
the lower compensation oil hole (16) and the upper compensation oil hole (18) are arranged in a staggered manner, an upper compensation oil hole pressing sheet (14) is arranged above the upper compensation oil hole (18), and the upper compensation oil hole pressing sheet (14) is of a structure which can cover the upper compensation oil hole (18) when in use and can be jacked open under the action of the oil jacking force in the compensation cavity (5) so that the upper compensation oil hole (18) is opened;
and a compensation lower oil hole pressing sheet (19) is arranged below the compensation lower oil hole (16), and the compensation lower oil hole pressing sheet (19) is a structure which can cover the compensation lower oil hole (16) when in use and can be jacked open under the action of the oil pressure of the lower oil cavity (4) so that the compensation lower oil hole (16) is opened.
4. The piston cylinder oil chamber damper as claimed in claim 2, wherein: the lower oil hole (21) is arranged around the upper oil hole (22);
the compensation upper oil hole (18) is arranged around the compensation lower oil hole (16).
5. The piston cylinder oil chamber damper as claimed in claim 4, wherein: an upper valve port pressing sheet connecting bolt (12) is arranged in the center of the piston valve port plate (9), a piston valve port upper pressing plate (11) and a piston valve port lower pressing plate (13) are arranged on the connecting bolt (12), the piston valve port upper pressing plate (11) can cover the area where the upper oil hole (22) is located, the piston valve port lower pressing plate (13) can cover the area where the lower oil hole (21) is located, and a hole (A) is reserved in the area corresponding to the upper oil hole (22);
the center of the lower piston valve plate (15) is provided with a lower valve port pressing sheet connecting bolt (17), the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are sleeved on the lower valve port pressing sheet connecting bolt (17), the compensation lower oil hole pressing sheet (19) can cover the region where the compensation lower oil hole (16) is located, the compensation upper oil hole pressing sheet (14) can cover the region where the compensation upper oil hole (18) is located, and a hole is reserved in the region corresponding to the compensation lower oil hole (16).
6. The piston cylinder oil chamber damper as claimed in claim 5, wherein: the piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13) are non-elastic plates or elastic plates;
when the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) are non-elastic plates: the piston valve port upper pressure plate (11) and the piston valve port lower pressure plate (13) are structures which can move along the upper valve port pressing plate connecting bolt (12) to control the opening and closing of the upper oil hole (22) and the lower oil hole (21);
when piston valve port top board (11) and piston valve port holding down board (13) are the elastic plate: the piston valve port upper pressing plate (11) and the piston valve port lower pressing plate (13) directly cover the upper oil hole (22) and the lower oil hole (21), and when the piston valve port upper pressing plate (11) or the piston valve port lower pressing plate (13) is impacted by oil, elastic deformation is generated to open the upper oil hole (22) or the lower oil hole (21).
7. The piston cylinder oil chamber damper as claimed in claim 5, wherein: the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are non-elastic plates or elastic plates;
when the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are non-elastic plates: the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are structures which can move along the lower valve port pressing sheet connecting bolt (17) to control the opening and closing of the compensation upper oil hole (18) and the compensation lower oil hole (16);
when the compensation upper oil hole pressing sheet (14) and the compensation lower oil hole pressing sheet (19) are elastic plates: the upper compensation oil hole pressing sheet (14) and the lower compensation oil hole pressing sheet (19) directly cover the upper compensation oil hole (18) and the lower compensation oil hole (16), and when the upper compensation oil hole pressing sheet (14) or the lower compensation oil hole pressing sheet (19) is impacted by oil, elastic deformation can be generated to open the upper compensation oil hole (18) or the lower compensation oil hole (16).
8. The piston cylinder oil chamber damper as claimed in claim 3, wherein: when the compensation cavity (5) is arranged on the periphery of the side wall of the lower oil cavity (4), a transition cavity (15-1) is formed at the bottom of the lower piston valve port plate (15), and the transition cavity (15-1) is communicated with the compensation cavity (5) through a channel (15-2) of the side wall.
9. The piston cylinder oil chamber damper as claimed in claim 1, wherein: a spiral spring (24) is sleeved outside the part, exposed out of the cavity shell (23), of the piston cylinder (1), the upper end of the spiral spring (24) is connected with an upper spring supporting seat (25), the lower end of the spiral spring (24) is connected with a lower spring supporting seat (26), a plurality of permanent magnets (2) are arranged on the outer wall of the piston cylinder (1), and a magnetic conduction ring (28) is arranged between every two adjacent permanent magnets (2); the two adjacent permanent magnets (2) are arranged in a way of opposite polarity;
the piston cylinder (1), the permanent magnet (2) and the magnetic conduction ring (28) form a secondary assembly, the secondary assembly penetrates through the primary assembly and can perform telescopic action relative to the primary assembly, the primary assembly comprises a primary outer cylinder (27), a primary winding (29) and a primary iron core (30), and the primary winding (29) and the primary iron core (30) are arranged in the primary outer cylinder (27) and are alternately arranged along the axial direction of the primary outer cylinder (27); the secondary assembly passes through the primary winding (29) and the primary iron core (30) and can do axial reciprocating movement relative to the primary winding (29) and the primary iron core (30).
10. The piston cylinder oil chamber damper as claimed in claim 9, wherein: a buffer block (31) is further arranged in the spiral spring (24), and the buffer block (31) is arranged between the spring upper supporting seat (25) and the primary outer cylinder (27).
CN202110326277.3A 2021-03-26 2021-03-26 Piston cylinder oil cavity damper Pending CN112963483A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110326277.3A CN112963483A (en) 2021-03-26 2021-03-26 Piston cylinder oil cavity damper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110326277.3A CN112963483A (en) 2021-03-26 2021-03-26 Piston cylinder oil cavity damper

Publications (1)

Publication Number Publication Date
CN112963483A true CN112963483A (en) 2021-06-15

Family

ID=76278587

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110326277.3A Pending CN112963483A (en) 2021-03-26 2021-03-26 Piston cylinder oil cavity damper

Country Status (1)

Country Link
CN (1) CN112963483A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL442504A1 (en) * 2022-10-12 2024-04-15 Politechnika Łódzka Dynamic vibration damper with adjustable magnetic stiffness

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL442504A1 (en) * 2022-10-12 2024-04-15 Politechnika Łódzka Dynamic vibration damper with adjustable magnetic stiffness

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