CN108953467B - Damping gap adjustable magneto-rheological damper with serial liquid flow channels - Google Patents
Damping gap adjustable magneto-rheological damper with serial liquid flow channels Download PDFInfo
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- CN108953467B CN108953467B CN201811111347.8A CN201811111347A CN108953467B CN 108953467 B CN108953467 B CN 108953467B CN 201811111347 A CN201811111347 A CN 201811111347A CN 108953467 B CN108953467 B CN 108953467B
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- 239000007788 liquid Substances 0.000 title claims abstract description 73
- 238000013016 damping Methods 0.000 title claims abstract description 59
- 238000004804 winding Methods 0.000 claims abstract description 49
- 230000005284 excitation Effects 0.000 claims abstract description 3
- 238000007789 sealing Methods 0.000 claims description 18
- 230000007704 transition Effects 0.000 claims description 14
- 230000005674 electromagnetic induction Effects 0.000 claims description 5
- 239000000696 magnetic material Substances 0.000 claims description 4
- 229910052799 carbon Inorganic materials 0.000 claims description 2
- 239000004020 conductor Substances 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 5
- 230000009467 reduction Effects 0.000 abstract description 5
- 230000009471 action Effects 0.000 abstract description 4
- 230000008859 change Effects 0.000 abstract description 2
- 239000012530 fluid Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 3
- 230000006698 induction Effects 0.000 description 2
- 229910001209 Low-carbon steel Inorganic materials 0.000 description 1
- 230000004308 accommodation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 230000003245 working effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/483—Arrangements for providing different damping effects at different parts of the stroke characterised by giving a particular shape to the cylinder, e.g. conical
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
- F16F9/537—Magnetorheological [MR] fluid dampers specially adapted valves therefor
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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
- F16F2234/00—Shape
- F16F2234/04—Shape conical
Abstract
The invention discloses a damping gap adjustable magnetorheological damper with a serial liquid flow channel, which mainly comprises a piston rod, an end cover, a cylinder body, a piston head, a valve core, an excitation coil, a winding frame and the like. The clearance between the valve core and the winding frame forms a conical liquid flow channel, the clearance between the outer cylinder body and the winding frame forms a circular liquid flow channel, the two form a serial liquid flow channel structure, and four sections of effective damping clearances can be formed under the action of a magnetic field. The liquid flow channel formed between the winding frame and the valve core can form two sections of conical effective damping gaps, the position of the valve core can be adjusted to change the thickness of the damping gaps, and the effect of adjusting the damping force is achieved. When the exciting coil is electrified to work, the damping force can be effectively controlled by controlling the current. The invention effectively increases the liquid flow damping length through the serial liquid flow channels, ensures that the damper can output damping force which is large enough and has wide adjustable range, and is particularly suitable for vibration reduction systems in the industries of railways, traffic and the like.
Description
Technical Field
The invention relates to a magnetorheological damper, in particular to a damper gap-adjustable magnetorheological damper with a series liquid flow channel.
Background
The magneto-rheological damper has the characteristics of millisecond response speed, large control range and large damping force output, so that the magneto-rheological damper becomes a semi-active executing device with excellent industrial application field. Currently, magneto-rheological dampers are widely applied to vibration reduction and shock resistance systems of buildings and bridges, vibration reduction of railway rolling stock and automobile suspension systems and the like.
The exciting coil of the magneto-rheological damper designed at present is often wound in the annular groove of the piston head, and an annular liquid flow channel is arranged in the piston head or between the outer surface of the piston and the inner surface of the cylinder body. When the magnetic field coil is electrified, a magnetic field perpendicular to the flowing direction of the magnetorheological fluid is generated in the annular liquid flow channel, and damping force is generated under the action of the magnetic field. Under the general condition, the magnitude of the loading current is changed, and the magnetic induction intensity generated at the magnetorheological fluid in the annular gap can be adjusted, so that the damping force of the magnetorheological damper is adjusted. When the magnetic induction intensity in the damping gap reaches saturation, the output damping force of the damper also reaches the maximum. The maximum damping force of the magnetorheological damper with the structure can be improved, the inner diameter of the damper cylinder body can be increased, the thickness of a damping gap can be changed, or measures such as multistage pistons can be adopted. But also brings some disadvantages: increasing the inner diameter of the damper cylinder body can lead to the increase of the overall dimension of the damper; the thickness of the damping gap is changed by adopting magneto-rheological dampers with different structures, and the thickness of the damping gap of the magneto-rheological damper designed at present is fixed and not adjustable, so that the application requirements under different working conditions are difficult to meet; when the damping length is increased by adopting the multistage piston structure to improve the output damping force, the axial size of the piston can be increased, and the effective working stroke of the damper can be reduced under the condition of a certain installation size.
Disclosure of Invention
In order to overcome the problems in the background art and meet the requirements of the magnetorheological damper in engineering application, the invention provides a damper clearance-adjustable magnetorheological damper with a series liquid flow channel. The outer surface of the valve core of the magnetorheological damper and the inner surface of the winding frame adopt a conical surface structure with a certain angle, and a gap between the valve core and the winding frame forms a conical liquid flow channel A. The outer surface of the winding frame and the inner surface of the outer cylinder body adopt smooth cylindrical surface structures, and a circular liquid flow channel B is formed by a gap between the outer cylinder body and the winding frame. The conical liquid flow channel A and the annular liquid flow channel B form a serial liquid flow channel structure, and four sections of effective damping gaps can be formed under the action of exciting current in the exciting coil. The conical liquid flow channel A formed between the spool and the spool can form two sections of conical effective damping gaps, the spool and the exciting coil form a single-coil magnetorheological valve structure with adjustable damping gaps, and the effective damping gap thickness of the conical liquid flow channel A can be changed by adjusting the position of the spool, so that the effect of adjusting the damping force when magnetorheological fluid flows through is achieved. When the exciting coil is electrified to work, the damping force can be effectively controlled by controlling the magnitude of the applied current. The invention effectively increases the liquid flow damping length through the structure with the adjustable serial liquid flow channel and the damping gap, provides the adjustable damping gap thickness, can realize the effective control of damping force by controlling the magnitude of the applied current in the exciting coil, ensures that the damper can output the damping force with enough large and wide adjustable range, and is particularly suitable for vibration reduction systems in the industries of railways, traffic and the like.
The technical scheme adopted by the invention for solving the technical problems comprises the following steps: the device comprises a left lifting lug (1), a piston rod (2), a left end cover (3), an outer cylinder body (4), a left inner cylinder body (5), a left taper pin (6), a piston head (7), a right taper pin (8), a valve core (9), a winding frame (10), an excitation coil (11), a right inner cylinder body (12), a right end cover (13), a lock nut (14) and a right lifting lug (15); the left end of the piston rod (2) is fixedly connected with the left lifting lug (1) through threads; a circular through hole is processed in the middle of the left end cover (3), and the piston rod (2) is in clearance fit with the inner surface of the circular through hole of the left end cover (3) and is sealed by a sealing ring; the left end cover (3) is in transition fit with the inner surface of the left inner cylinder body (5) and is sealed by a sealing ring; the left end cover (3) is fixedly connected with the left inner cylinder body (5) through screws; the outer cylinder body (4) is in transition fit with the outer surface of the left inner cylinder body (5) and is sealed by a sealing ring; the left end cover (3) is fixedly connected with the outer cylinder body (4) through screws; the middle part of the piston rod (2) is provided with a circular bulge, and the circumferential inner surface of the piston head (7) is in transition fit with the circular bulge of the piston rod (2); the left end of the piston head (7) and the piston rod (2) are axially positioned through a left taper pin (6); the right end of the piston head (7) and the piston rod (2) are axially positioned through a right taper pin (8); the outer surface of the piston head (7) is in clearance fit with the inner surface of the left inner cylinder body (5) and is sealed by a sealing ring; the left end of the winding frame (10) is in transition fit with the outer surface of the left inner cylinder body (5) and is sealed by a sealing ring; the right end of the winding frame (10) is in transition fit with the outer surface of the right inner cylinder body (12) and is sealed by a sealing ring; the exciting coil (11) is wound in a winding groove (1001) of the winding frame (10), and leads of the exciting coil are led out of the damper from a lead hole (1301) of the right end cover (13) through a lead groove (1201) of the right inner cylinder body (12); the center part of the valve core (9) is provided with a stepped hole (903), the left end of the valve core is provided with a circular boss (901), and the circular boss (901) at the left end of the valve core (9) is in clearance fit with the right end of the piston rod (2) and is sealed by a sealing ring; the right side of the valve core (9) is provided with external threads, can be in threaded connection with an internal threaded hole formed in the middle of the right end cover (13), and is mechanically locked and positioned through a locking nut (14); the right end of the piston rod (2) can move left and right in a central stepped hole (903) of the valve core (9); the left working part of the valve core (9) is designed into a truncated cone shape, and a conical outer surface (902) with a certain angle is formed; the right side of the valve core (9) is provided with a through hole (904), and the through hole (904) is connected with the atmosphere, so that the air pressure in the central stepped hole (903) is unchanged when the right end of the piston rod (2) moves left and right in the central stepped hole (903) of the valve core (9); the right end of the valve core (9) is provided with a pin hole (905) corresponding to the pin hole on the right lifting lug (15) and can be connected with a cross wrench; the outer surface (902) of the valve core (9) and the inner surface (1002) of the winding frame (10) adopt conical surface structures with certain angles, and a conical liquid flow channel A is formed by a gap between the outer surface (902) of the valve core (9) and the inner surface (1002) of the winding frame (10); the outer surface of the winding frame (10) and the inner surface of the outer cylinder body (4) adopt smooth cylindrical surface structures, the gap between the two is 1mm, and a circular liquid flow channel B is formed by the gap between the outer surface of the winding frame (10) and the inner surface of the outer cylinder body (4); the conical liquid flow channel A and the annular liquid flow channel B form a serial liquid flow channel structure; when exciting current with a certain magnitude is introduced into the exciting coil (11), magnetic force lines generated by electromagnetic induction reach the valve core (9) through the outer cylinder body (4), the annular liquid flow channel B, the winding frame (10) and the conical liquid flow channel A, and then return to the outer cylinder body (4) through the conical liquid flow channel A, the winding frame (10) and the annular liquid flow channel B to form a closed loop; at the moment, four sections of effective damping gaps I, II, III and IV are formed in the serial liquid flow channel; the right end cover (13) is in transition fit with the inner surface of the right inner cylinder body (12) and is sealed by a sealing ring; the right end cover (13) is fixedly connected with the right inner cylinder body (12) through screws; the outer cylinder body (4) is in transition fit with the outer surface of the right inner cylinder body (12) and is sealed by a sealing ring; the right end cover (13) is fixedly connected with the outer cylinder body (4) through a screw; the right lifting lug (15) is fixedly connected with the right end of the valve core (9) through threads; the left end face of the left inner cylinder body (5) is provided with 5 circumferentially uniformly arranged internal threaded holes, and the left end face of the left inner cylinder body corresponds to 5 circular through holes formed in the left end cover (3) and can be in positioning connection with the left end cover (3) through screws; the outer surface of the left side of the left inner cylinder body (5) is uniformly provided with 5 circular diversion through holes in the circumferential direction, and the circular diversion through holes play a role in communicating the left cavity of the piston head (7) with the right cavity of the piston head (7); the right end face of the right inner cylinder body (12) is provided with 5 circumferentially uniformly arranged internal threaded holes, and the corresponding 5 circular through holes on the right end cover (13) can play a role in positioning connection with the right end cover (13) through screws; the outer surface of the right side of the right inner cylinder body (12) is uniformly provided with 5 circular diversion through holes in the circumferential direction, and the circular diversion through holes play a role in communicating the right cavity of the piston head (7) with the left cavity of the piston head (7); the valve core (9), the winding frame (10) and the exciting coil (11) form a single-coil magneto-rheological valve structure with an adjustable damping gap, and the damping gap thickness of the conical liquid flow channel A can be changed by adjusting the position of the valve core (9), so that the damping force of magneto-rheological liquid flowing through the valve core is adjusted; the outer cylinder body (4), the valve core (9) and the winding frame (10) are respectively made of low-carbon magnetic conductive materials; the rest parts are made of non-magnetic materials.
Compared with the background technology, the invention has the following beneficial effects:
(1) The magnetorheological damper adopts a serial liquid flow channel structure, and can obtain larger controllable damping force under the action of smaller exciting current on the premise of not increasing the external dimension of the magnetorheological damper. Compared with a magneto-rheological damper with a single annular liquid flow channel, the magneto-rheological damper has wider dynamic damping force adjusting range and is particularly suitable for vibration reduction systems in the industries of railways, traffic and the like.
(2) When exciting current with a certain magnitude is introduced into the exciting coil, magnetic force lines generated by electromagnetic induction reach the valve core through the outer cylinder body, the annular liquid flow channel B, the winding frame and the conical liquid flow channel A, and then return to the outer cylinder body through the conical liquid flow channel A, the winding frame and the annular liquid flow channel B to form a closed loop; in the closed magnetic field loop, four sections of effective damping gaps I, II, III and IV are formed at the positions of the serial liquid flow channels, and the magnetic field performance is fully utilized.
(3) Compared with a conventional magnetorheological damper with fixed damping gap, the conical liquid flow channel A formed between the spool and the spool of the magnetorheological damper can form two sections of conical effective damping gaps; the valve core, the winding frame and the exciting coil form a single-coil magneto-rheological valve structure with adjustable damping gap; the effective damping clearance distance of toper that forms between case and the bobbin is adjustable, and the damping force size when adjusting the position of case can change magnetorheological fluid and flow through makes its damping force accommodation wider, and magnetorheological damper working property is better.
(4) The parts of the magnetorheological damper are except for the cylinder body, the valve core and the winding frame, and the rest parts are made of non-magnetic materials except for the low-carbon steel magnetic materials. The design can effectively ensure that magnetic lines of force are distributed in four sections of effective damping gaps as intensively as possible, fully exert the effect of a vertical magnetic field on magnetorheological fluid, improve the efficiency of the magnetorheological damper and effectively reduce the energy consumption of the magnetorheological damper.
Drawings
Fig. 1 is a schematic diagram of the structure of the present invention.
Fig. 2 is a cross-sectional view of the right end cap of the present invention.
Fig. 3 is a left side view of the right end cap of the present invention.
Fig. 4 is a cross-sectional view of a bobbin of the present invention.
Fig. 5 is a cross-sectional view of a valve cartridge of the present invention.
Fig. 6 is a cross-sectional view of the left inner cylinder of the present invention.
Fig. 7 is a right side view of the left inner cylinder of the present invention.
Fig. 8 is a cross-sectional view of the right inner cylinder of the present invention.
Fig. 9 is a left side view of the right inner cylinder of the present invention.
Fig. 10 is a distribution diagram of magnetic lines of force when the present invention is energized.
Detailed Description
The invention is further illustrated by the following examples in conjunction with the accompanying drawings:
fig. 1 is a schematic diagram of the structure of the present invention. Mainly comprises the following steps: the left lifting lug 1, the piston rod 2, the left end cover 3, the outer cylinder body 4, the left inner cylinder body 5, the left taper pin 6, the piston head 7, the right taper pin 8, the valve core 9, the winding frame 10, the exciting coil 11, the right inner cylinder body 12, the right end cover 13, the locking nut 14 and the right lifting lug 15.
Fig. 2 is a cross-sectional view of the right end cap of the present invention, and fig. 3 is a left side view of the right end cap of the present invention. The center of the right end face of the right end cover 13 is provided with a circular through hole which can axially position the left end of the piston rod 2; the outer ring of the right end face of the right end cover 13 is provided with 6 circular through holes which are uniformly distributed along the circumferential direction, and the outer ring corresponds to 6 threaded holes on the left end face of the outer cylinder body 4, and can play a role in positioning and connecting with the outer cylinder body 4 through screws; the inner ring of the right end face of the right end cover 13 is provided with 5 circular through holes which are uniformly distributed along the circumferential direction, and the circular through holes correspond to 5 threaded holes on the left end face of the left inner cylinder body 5, and can play a role in positioning and connecting with the left inner cylinder body 5 through screws; the right end face of the right end cover 13 is provided with a lead hole 1301, and the lead of the exciting coil 11 can be led out of the lead hole 1301 corresponding to the lead groove 1201 on the right inner cylinder body 12.
Fig. 4 shows a cross-sectional view of the bobbin of the present invention. The bobbin 10 is provided with a winding groove 1001, the exciting coil 11 is wound in the winding groove 1001 on the bobbin 10, and a lead wire of the exciting coil is led out of the damper from a lead wire hole 1301 of the right end cover 13 through a lead wire groove 1201 of the right inner cylinder body 12; the middle part of the bobbin 10 is designed as a circular truncated cone-shaped through hole, forming a conical inner surface 1002.
Figure 5 shows a cross-sectional view of a valve cartridge of the present invention. The center part of the valve core 9 is provided with a stepped hole 903, the left end of the valve core 9 is provided with a circular boss 901, and the right end of the piston rod 2 can move left and right in the stepped hole 903 in the center of the valve core 9; the left working part of the valve core 9 is designed into a truncated cone shape, and a conical outer surface 902 with a certain angle is formed; the right side of the valve core 9 is provided with a through hole 904, and the through hole 904 is connected with the atmosphere, so that the air pressure in the center stepped hole 903 is unchanged when the right end of the piston rod 2 moves left and right in the center stepped hole 903 of the valve core 9; the right end of the valve core 9 is provided with a pin hole 905 which corresponds to the pin hole on the right lifting lug 15 and can be connected with a cross wrench.
Fig. 6 is a cross-sectional view of the left inner cylinder of the present invention, and fig. 7 is a right side view of the left inner cylinder of the present invention. The left end face of the left inner cylinder body 5 is provided with 5 threaded holes which are uniformly distributed along the circumferential direction, and the left end face of the left inner cylinder body corresponds to 5 circular through holes formed in the left end cover 3, and can be in positioning connection with the left end cover 3 through screws; the left outer surface of the left inner cylinder body 5 is uniformly provided with 5 circular diversion through holes in the circumferential direction, and the circular diversion through holes play a role in communicating the left cavity of the piston head 7 with the right cavity of the piston head 7.
Fig. 8 is a cross-sectional view of the right inner cylinder of the present invention, and fig. 9 is a left side view of the right inner cylinder of the present invention. The right end face of the right inner cylinder body 12 is provided with 5 circumferentially uniformly arranged internal threaded holes, and the corresponding 5 round through holes are formed in the right end cover 13, so that the positioning connection effect with the right end cover 13 can be achieved through screws; the outer surface of the right side of the right inner cylinder body 12 is uniformly provided with 5 circular diversion through holes in the circumferential direction, and the circular diversion through holes play a role in communicating the right cavity of the piston head 7 with the left cavity of the piston head 7.
Fig. 10 shows the distribution of magnetic lines of force during the energizing operation of the present invention. The outer surface 902 of the valve core 9 and the inner surface 1002 of the winding frame 10 adopt a conical surface structure with a certain angle, and a conical liquid flow channel A is formed between the valve core and the conical surface structure; the outer surface of the winding frame 10 and the inner surface of the outer cylinder body 4 adopt smooth cylindrical surface structures, a gap between the two is 1mm, and a circular liquid flow channel B is formed between the two gaps; the conical liquid flow channel A and the annular liquid flow channel B form a serial liquid flow channel structure; when exciting current with a certain magnitude is introduced into the exciting coil 11 to work, magnetic force lines generated by electromagnetic induction reach the valve core 9 through the outer cylinder body 4, the annular liquid flow channel B, the winding frame 10 and the conical liquid flow channel A, and then return to the outer cylinder body 4 through the conical liquid flow channel A, the winding frame 10 and the annular liquid flow channel B to form a closed loop; at this time, four sections of effective damping gaps I, II, III and IV are formed at the positions of the serial liquid flow channels.
The working principle of the invention is as follows:
as shown in fig. 6, 7, 8, 9 and 10, the outer surface 902 of the valve core 9 and the inner surface 1002 of the spool 10 adopt a tapered surface structure having a certain angle, and a gap between the outer surface 902 of the valve core 9 and the inner surface 1002 of the spool 10 forms a tapered flow passage a. The outer surface of the winding frame 10 and the inner surface of the outer cylinder body 4 adopt smooth cylindrical surface structures, the gap between the two is 1mm, and a circular liquid flow channel B is formed by the gap between the outer surface of the winding frame 10 and the inner surface of the outer cylinder body 4. The conical flow channel A and the annular flow channel B form a serial flow channel structure. When exciting current with a certain magnitude is introduced into the exciting coil 11, magnetic force lines generated by electromagnetic induction reach the valve core 9 through the outer cylinder body 4, the annular liquid flow channel B, the winding frame 10 and the conical liquid flow channel A, and then return to the outer cylinder body 4 through the conical liquid flow channel A, the winding frame 10 and the annular liquid flow channel B to form a closed loop. At this time, four sections of effective damping gaps I, II, III and IV are formed at the positions of the serial liquid flow channels. The conical liquid flow channel A formed between the spool 10 and the spool 9 can form two sections of conical effective damping gaps, the spool 9, the spool 10 and the exciting coil 11 form a single-coil magneto-rheological valve structure with adjustable damping gaps, and the effective damping gap thickness of the conical liquid flow channel A can be changed by adjusting the position of the spool 9, so that the effect of adjusting the damping force when magneto-rheological liquid flows through is achieved.
Claims (4)
1. A damper gap-adjustable magnetorheological damper having a series flow channel, comprising: the device comprises a left lifting lug (1), a piston rod (2), a left end cover (3), an outer cylinder body (4), a left inner cylinder body (5), a left taper pin (6), a piston head (7), a right taper pin (8), a valve core (9), a winding frame (10), an excitation coil (11), a right inner cylinder body (12), a right end cover (13), a lock nut (14) and a right lifting lug (15); the left end of the piston rod (2) is fixedly connected with the left lifting lug (1) through threads; a circular through hole is processed in the middle of the left end cover (3), and the piston rod (2) is in clearance fit with the inner surface of the circular through hole of the left end cover (3) and is sealed by a sealing ring; the left end cover (3) is in transition fit with the inner surface of the left inner cylinder body (5) and is sealed by a sealing ring; the left end cover (3) is fixedly connected with the left inner cylinder body (5) through screws; the outer cylinder body (4) is in transition fit with the outer surface of the left inner cylinder body (5) and is sealed by a sealing ring; the left end cover (3) is fixedly connected with the outer cylinder body (4) through screws; the middle part of the piston rod (2) is provided with a circular bulge, and the circumferential inner surface of the piston head (7) is in transition fit with the circular bulge of the piston rod (2); the left end of the piston head (7) and the piston rod (2) are axially positioned through a left taper pin (6); the right end of the piston head (7) and the piston rod (2) are axially positioned through a right taper pin (8); the outer surface of the piston head (7) is in clearance fit with the inner surface of the left inner cylinder body (5) and is sealed by a sealing ring; the left end of the winding frame (10) is in transition fit with the outer surface of the left inner cylinder body (5) and is sealed by a sealing ring; the right end of the winding frame (10) is in transition fit with the outer surface of the right inner cylinder body (12) and is sealed by a sealing ring; the exciting coil (11) is wound in a winding groove (1001) of the winding frame (10), and leads of the exciting coil are led out of the damper from a lead hole (1301) of the right end cover (13) through a lead groove (1201) of the right inner cylinder body (12); the center part of the valve core (9) is provided with a stepped hole (903), the left end of the valve core is provided with a circular boss (901), and the circular boss (901) at the left end of the valve core (9) is in clearance fit with the right end of the piston rod (2) and is sealed by a sealing ring; the right side of the valve core (9) is provided with external threads, can be in threaded connection with an internal threaded hole formed in the middle of the right end cover (13), and is mechanically locked and positioned through a locking nut (14); the right end of the piston rod (2) can move left and right in a central stepped hole (903) of the valve core (9); the left working part of the valve core (9) is designed into a truncated cone shape, and a conical outer surface (902) with a certain angle is formed; the right side of the valve core (9) is provided with a through hole (904), and the through hole (904) is connected with the atmosphere, so that the air pressure in the central stepped hole (903) is unchanged when the right end of the piston rod (2) moves left and right in the central stepped hole (903) of the valve core (9); the right end of the valve core (9) is provided with a pin hole (905) corresponding to the pin hole on the right lifting lug (15) and can be connected with a cross wrench; the outer surface (902) of the valve core (9) and the inner surface (1002) of the winding frame (10) adopt conical surface structures with certain angles, and a conical liquid flow channel A is formed by a gap between the outer surface (902) of the valve core (9) and the inner surface (1002) of the winding frame (10); the outer surface of the winding frame (10) and the inner surface of the outer cylinder body (4) adopt smooth cylindrical surface structures, the gap between the two is 1mm, and a circular liquid flow channel B is formed by the gap between the outer surface of the winding frame (10) and the inner surface of the outer cylinder body (4); the conical liquid flow channel A and the annular liquid flow channel B form a serial liquid flow channel structure; when exciting current with a certain magnitude is introduced into the exciting coil (11), magnetic force lines generated by electromagnetic induction reach the valve core (9) through the outer cylinder body (4), the annular liquid flow channel B, the winding frame (10) and the conical liquid flow channel A, and then return to the outer cylinder body (4) through the conical liquid flow channel A, the winding frame (10) and the annular liquid flow channel B to form a closed loop; at the moment, four sections of effective damping gaps I, II, III and IV are formed in the serial liquid flow channel; the right end cover (13) is in transition fit with the inner surface of the right inner cylinder body (12) and is sealed by a sealing ring; the right end cover (13) is fixedly connected with the right inner cylinder body (12) through screws; the outer cylinder body (4) is in transition fit with the outer surface of the right inner cylinder body (12) and is sealed by a sealing ring; the right end cover (13) is fixedly connected with the outer cylinder body (4) through a screw; the right lifting lug (15) is fixedly connected with the right end of the valve core (9) through threads.
2. The adjustable damping gap magnetorheological damper of claim 1, wherein the damper comprises a series flow channel, wherein: the left end face of the left inner cylinder body (5) is provided with 5 circumferentially uniformly arranged internal threaded holes, and the left end face of the left inner cylinder body corresponds to 5 circular through holes formed in the left end cover (3) and can be in positioning connection with the left end cover (3) through screws; the outer surface of the left side of the left inner cylinder body (5) is uniformly provided with 5 circular diversion through holes in the circumferential direction, and the circular diversion through holes play a role in communicating the left cavity of the piston head (7) with the right cavity of the piston head (7); the right end face of the right inner cylinder body (12) is provided with 5 circumferentially uniformly arranged internal threaded holes, and the corresponding 5 circular through holes on the right end cover (13) can play a role in positioning connection with the right end cover (13) through screws; the outer surface of the right side of the right inner cylinder body (12) is uniformly provided with 5 circular diversion through holes in the circumferential direction, and the circular diversion through holes are used for communicating the right cavity of the piston head (7) with the left cavity of the piston head (7).
3. The adjustable damping gap magnetorheological damper of claim 1, wherein the damper comprises a series flow channel, wherein: the valve core (9), the winding frame (10) and the exciting coil (11) form a single-coil magneto-rheological valve structure with an adjustable damping gap, and the damping gap thickness of the conical liquid flow channel A can be changed by adjusting the position of the valve core (9), so that the damping force of magneto-rheological liquid flowing through the valve core is adjusted.
4. The adjustable damping gap magnetorheological damper of claim 1, wherein the damper comprises a series flow channel, wherein: the outer cylinder body (4), the valve core (9) and the winding frame (10) are respectively made of low-carbon magnetic conductive materials; the rest parts are made of non-magnetic materials.
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