GB2112104A - Adjusting hydraulic dampers - Google Patents
Adjusting hydraulic dampers Download PDFInfo
- Publication number
- GB2112104A GB2112104A GB08232113A GB8232113A GB2112104A GB 2112104 A GB2112104 A GB 2112104A GB 08232113 A GB08232113 A GB 08232113A GB 8232113 A GB8232113 A GB 8232113A GB 2112104 A GB2112104 A GB 2112104A
- Authority
- GB
- United Kingdom
- Prior art keywords
- piston
- piston rod
- rod
- actuating rod
- valve member
- 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.)
- Withdrawn
Links
- 238000013016 damping Methods 0.000 claims abstract description 27
- 239000007788 liquid Substances 0.000 claims abstract description 10
- 230000008602 contraction Effects 0.000 claims abstract description 6
- 238000000638 solvent extraction Methods 0.000 claims abstract description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Classifications
-
- 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
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/461—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall characterised by actuation means
- F16F9/462—Rotary actuation means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Reciprocating, Oscillating Or Vibrating Motors (AREA)
Abstract
A hydraulic damper comprises a cylinder 1, a piston 13 working in the cylinder and partitioning the interior thereof into two liquid chambers 17, 18, a damping force generating valve device 28, 32 mounted on the piston for generating the damping force both in the extension and contraction strokes of the damper, a piston rod 15 secured to the piston, a coaxial bore 20 and a radial hole 21 formed in the piston rod to constitute a by-pass passage 19 connecting the two liquid chambers, a rotatably adjustable valve member 43 for steppingly controlling the effective area of the by-pass passage, and an actuating rod 41 secured to the valve member and extending through the coaxial bore in the piston rod. The operating mechanism for rotating the valve member 43 comprises a supporting member 55 mounted on the piston rod for mounting thereon at least two electromagnets 58, 59, 60, a magnetizable member 57 connected to the actuating rod 41, and an electric circuit for selectively energizing the electromagnets thereby attracting the magnetizable member, and thereby moving the valve member 43 to a selected position. <IMAGE>
Description
SPECIFICATION
Hydraulic damper
This invention relates to hydraulic dampers
adapted for use in a suspension system of a
vehicle and, particularly to hydraulic dampers of
the kind including a generally vertical cylinder
receiving therein hydraulic liquid, a piston working
in the cylinder and partitioning the interior thereof
into two liquid chambers, one or a pair of damping force generating valves mounted on the piston for
generating the damping force both in the
extension and contraction strokes of the damper, a
piston rod secured to the piston and extending through the upper end of the cylinder to the outside, a coaxial bore and a radial hole formed in the piston rod to constitute a by-pass passage connecting the two liquid chambers, an adjustable valve member for steppingly controlling the effective area of the by-pass passage, and an actuating rod extending through the coaxial bore in the piston rod with the inner end thereof being secured to the valve member.
By adjusting the damping force of the damper, it is possible to improve the comfortableness when the vehicle is running on a smooth road and to prevent the excessive vertical movement of the body of the vehicle when the vehicle is running on a rough road and to reliably control the direction or the heading of the vehicle. It will be understood that when the damping force is small the damper acts softly but the amplitude of the reciprocation is large and which sometimes deteriorates the inherent tendency maintaining the running direction of the vehicle.
In mounting hydraulic dampers of aforementioned damping force adjustable type on the vehicle, it is necessary to provide a suitable operating mechanism on the vehicle which is simple in construction, reliable in operation and easily be accessible by the driver of the vehicle.
This invention provides a hydraulic damper satisfying the aforesaid requirements and, the hydraulic damper according to the invention further comprises:
the adjustable valve member being rotatable around the axis of the actuating rod and having an arcuate outer surface extending along the circumference thereof,
a generally cylindrical surface slidably engaging with the arcuate outer surface of the valve member constituting a part of the by-pass passage,
one or more radial holes formed in the cylindrical surface also constituting a part of the by-pass passage,
a supporting member mounted on the upper end of the piston rod,
a magnetizable member secured to the upper end of the actuating rod to extend transversely with respect to the axis of the actuating rod,
a plurality of electromagnets mounted on the supporting member and spaced with each other in the direction of the circumference of a circle with the center of which aligning with the axis of the actuating rod, and
an electric circuit for selectively connecting either one of the electromagnets with an electric source, whereby said selected electromagnet attracts the magnetizable member with the actuating rod turning around the axis thereof.
The adjustment is preferably effected at two or three steps although it is possible to adjust the damping force of the damper at four or more steps.
The invention will now be explained in detail with reference to the accompanying drawings exemplifying a preferred embodiment of the invention, in which:
Fig. 1 is a longitudinal sectional view of a hydraulic damper according to the invention;
Fig. 2 is a schematic explanatory view of an operating mechanism for the damper of Fig. 1;
Fig. 3 is a sectional view taken along line Ill-Ill in Fig. 1,and Fig. 4 is a diagram showing the damping force characteristics of the damper.
The hydraulic damper shown in the drawings comprises a tubular main body 1 consisting of an outer tube 2, an inner tube 3 constituting the cylinder according to the invention, a bottom cap 4 closing the lower end of the outer tube 2, and an upper cap 5 closing the upper end of the outer tube 2. The inner and outer tubes 2 and 3 define therebetween an annular space serving as a reservoir 6. The reservoir 6 communicates with the interior of the inner tube 3 through a connecting hole 7 provided in the lower end portion of the inner tube 3. A mounting ring 8 is secured to the bottom cap 4. A rod guide 9 closes the upper end of the inner tube 3 and slidably guides a piston rod 1 5 which will hereinafter be explained.An annular seal 12, a seal 11 serving as a check valve encircling the piston rod 1 5 and normally seating on the rod guide 9 to allow the fluid flow only in the radially outward direction with respect to the piston rod and toward the reservoir 6, and a spring 10 are disposed between the upper cap 5 and the rod guide 9.
A piston 1 3 is slidably fitted in the inner tube 3, and a coaxial bore 14 is formed in the piston 13 for fitting with the piston rod 1 5. The piston rod 1 5 is secured to the piston 13 with a reduced diameter portion of the piston rod 1 5 fitting with the bore 14, and a hollow nut 1 6 screwthreadingly engaging with the tip end of the small diameter portion. The piston 1 3 partitions the interior of the inner tube 3 into a first chamber or the upper chamber 17 and a second or the lower chamber 1 8. The piston rod 1 5 extends through the upper chamber 17, slidably through the rod guide 9 and the seal 1 2 to the outside of the damper.The chambers 17 and 18, and the lower portion of the reservoir 6 contain therein hydraulic liquid such as oil, and the upper portion of the reservoir 6 contains therein gas under pressure.
A coaxial bore 20 extends through the piston rod 1 5 with the lower end thereof opening to the interior of the hollow nut 16. A radial hole 21 connects the bore 20 with the upper chamber 1 7.
The interior of the hollow nut 1 6 is connectable to the lower chamber 18 through radial holes 45 and 46. Thus, the radial hole 21 in the piston rod, the coaxial bore 20 in the piston rod, and the radial holes 45 and 46 in the hollow nut 1 6 constitute a by-pass passage 1 9 according to the invention which communicates the upper and lower chambers 1 7 and 1 8 by-passing the damping force generating valves mounted on the piston which will be explained hereinafter.
Annular grooves 24 and 25 are respectively formed in the upper and lower end surfaces of the piston 13, and the grooves 24 and 25 are respectively permanently connected to the lower and upper chambers 18 and 1 7 through a plurality of connecting holes 27 and 26 respectively (although only one each is shown in Fig. 1). On the upper side of the piston 1 3, there is provided a damping force generating valve 28 for the contraction stroke.The damping force generating valve 28 consists of a valve disc 29 consisting of two or more mutually overlapping annular sheets normally covering the annular groove 24, an annular retainer 30 acting as a fulcrum of the deflection of the valve disc 29, a retainer 31 having an increased diameter for preventing the excessive deflection of the valve disc 29, and a valve seat defined on the outer edge of the circumference of the groove 24. The valve disc 29 and the retainers 30 and 31 are clamped between the piston 13 and a shoulder 1 5a which is formed on the piston rod 15. Similarly, a damping force generating valve 32 for the extension stroke is provided on the lower side of the piston.The valve 32 consists of a valve disc 33 consisting of two or more overlapping discs and normally covering the annular groove 25 in the piston 13, a retainer 34 serving as a fulcrum of the deflection of the valve disc 33, a retainer 35 having an increased diameter for preventing the excessive deflection of the valve disc 33, and a valve seat defined on the outer edge of the circumference of the groove 25.
The valve disc 33 and the retainers 34 and 35 are clamped between the piston 1 3 and the hollow nut 16.
An actuating rod 41 extends loosely through the bore 20 in the piston rod 1 5. The upper end of the rod 41 projects from the upper end of the piston rod 1 5. A seal 42 is provided between the rod 41 and the upper end portion of the bore 20 for allowing the rotation of the rod 41 around the longitudinal axis thereof but preventing the leakage of the hydraulic liquid. The lower or the
inner end of the rod 41 projects from the piston
rod 1 5 and is secured to a closure member 43.
The closure member 43 comprises a disc shaped portion having a substantial thickness and slidably and rotatably engaging with the inner peripheral surface of the hollow nut 16, and a partially cylindrical or arcuate portion (Fig. 3) slidably engaging with the inner peripheral surface of the nut 1 6. A plurality of communicating holes 51 are formed in the disc shaped portion of the closure member 43. A stop 47 is provided in the hollow nut 1 6 to restrict the range of the relative rotation
between the closure member 43 and the nut 16.
The partially cylindrical portion of the closure
member 43 selectively opens and closes the radial
holes 45 and 46 in the wall of the nut 16 in
response to the reciprocating rotation of the
actuating rod 41. A plurality of rings 48 are
disposed between the closure member 43 and a
shoulder 1 6a formed in the nut 16, and a spring
50 is disposed between the closure member 43
and a cap 49 closing the lower end of the hollow
nut 16. The spring 50 urges the closure member
43 against the rings 48 to maintain the relative
vertical position of the closure member 43 with
respect to the hollow nut 1 6.
The upper end of the piston rod 1 5 is inserted
through the chassis 53 (only a portion thereof is
shown in Fig. 1) of a vehicle such as an
automobile and is secured thereto through a nut
52 screw-threadingly engaging with a reduced
diameter upper end portion of the piston rod 1 5.
Incidentally, the mounting ring 8 is secured to
such as a wheel shaft of the vehicle.
A mounting member 54 is also secured to the
upper end portion of the piston rod 1 5, and a table
55 is mounted on the mounting member 54. A
rotatable shaft 56 is rotatably mounted on the table 55 and is connected to the tip end of the
actuating rod 41 so as to integrally rotate therewith around a common longitudinal axis. A
magnetizable member 57 such as an iron bar, a bar magnet or the like is mounted on the rotatable shaft 56. Three sets of solenoids 58-1, 58-2; 59-1, 59-2; 60-1, 60-2 are mounted on the table 55 on the radially outer sides of the magnetizable member, and being spaced from each other along the circumference of a circle encircling the shaft 56.Each set of the solenoids consists of diametrically opposingly arranged two solenoids in the embodiment, however, it is possible to omit the solenoids 58-2, 59-2 and 60-2. Each set of solenoids is selectably connected to an electric source 61 through a switch 62.
The hydraulic damper of adjustable damping force type having the constitution as described heretofore operates as follows. Fig. 4 is a diagram showing the damping force characteristics wherein damping force W1 in the extension stroke and damping force W2 in the contraction stroke are shown with reference to the piston speed V.
Firstly, it is assumed that the solenoids 58-1 and 58-2 are energized, thereby the magnetizable member 57 is attracted to take the condition shown in Fig. 2 with the closure member 43 taking the condition of Fig. 3. The connecting holes 45 and 46 are closed and the effective area of the by-pass passage is at the minimum. The damping force at that condition is shown by lines
OD and Od. It will be understood that the rising up portions or portions OD1 and Odr in lines OD and
Od are determined by the fixed orifice which permanently connects the chambers 17 and 18, and the valve discs 33 and 29 respectively start to separate from corresponding valve seats.
When solenoids 58-1 and 58-2 are deenergized and solenoids 59-1 and 59-2 are energized by operating the switch 62, the magnetizable member 57 rotates to oppose with the energized solenoids 59-1 and 59-2 with the closure member 45 rotating therewith. The connecting hole 45 opens, thus, the communication between the upper and lower chambers 17 and 18 in the extension and contraction stroke is easier than the first case. The damping force at this condition are depicted by lines OE and Oe in Fig. 4.
Thirdly, the solenoids 59-1, 59-2, 58-1 and 58-2 are deenergized and the solenoids 60-1 and 60-2 are energized by operating the switch 62. The magnetizable member 57 together with the actuating rod 41 and the closure member 43 rotates thereby opening the connecting holes 45 and 46. The effective area of the by-pass passage further increases, and the piston rod 15 can reciprocate more easily with the damping force being depicted by lines OF and Of in Fig. 4.
It will be understood that the electric current in the solenoids is preferably controlled such that a relatively large electric power is supplied to the solenoids in rotating the magnetizable member and that a relatively weak electric power is supplied in maintaining the magnetizable member at the rotated condition.
Accordingly, when the vehicle is running on a rough road, it is possible to obtain the optimum damping force by energizing the solenoids 58-1 and 58-2 whereby the excessive vertical movement or vibration of the vehicle can be prevented. When the vehicle is running on a smooth road, it is possible to obtain the optimum damping force by energizing the solenoids 60-1 and 60-2. Further, when the vehicle is running on a road of the condition intermediate between the smooth and rough, or on a smooth road at a high speed, it is preferable to energize the solenoids 59-1 and 59-2, thereby maintaining relatively comfortable driving condition and assuring a good response in controlling the vehicle.
In the embodiment, the damping force is adjusted in three steps, but the damping force can be adjusted to four or more steps. Further, the solenoids 58-1 and 58-2 may be omitted by providing resilient means such as a coil spring or the like normally biasing the closure member 43 in the fully closed condition.
In the embodiment, the closure member 43 cooperates with communcating holes 45 and 46 provided in the hollow nut 16, however, the closure member 43 may be modified to cooperate with the radial hole 21. In such case the radial
hole 21 in the piston rod 1 5 preferably consists of two or more small holes for selectively opened or
closed by the closure member 43.
As described heretofore, according to the
invention, a rotatably adjustable valve member for steppingly controlling the effective area of the bypass passage is connected to an actuating rod which extends through the coaxial bore in the piston rod, and the actuating rod is steppingly rotated by an operating mechanism including a plurality of electromagnets and an electric circuit for selectively energizing either one of the electromagnets. Therefore, the damping force of the damper can be adjusted very easily by the driver of the vehicle at desired time. The operating mechanism is very simple in the construction and cheap in the costs.
Claims (2)
1. A hydraulic damper including a generally vertical cylinder receiving therein hydraulic liquid, a piston working in the cylinder and partitioning the interior thereof into two liquid chambers, one or a pair or damping force generating valves mounted on the piston for generating the damping force both in the extension and contraction strokes of the damper, a piston rod secured to the piston and extending through the upper end of the cylinder to the outside, a coaxial bore and a radial hole formed in the piston rod to constitute a bypass passage connecting said two liquid chambers, an adjustable valve member for steppingly controlling the effective area of the bypass passage, and an actuating rod extending through said coaxial bore in the piston rod with the inner end thereof being secured to said valve member, characterized by
said adjustable valve member being rotatable around the axis of said actuating rod and having an arcuate outer surface extending along the circumference thereof,
a generally cylindrical surface slidably engaging with the arcuate outer surface of the valve member constituting a part of said by-pass passage,
one or more radial holes formed in the cylindrical surface also constituting a part of said by-pass passage,
a supporting member mounted on the upper
end of said piston rod,
a magnetizable member secured to the upper
end of the actuating rod to extend transversely with respect to the axis of said actuating rod,
a plurality of electromagnets mounted on the
supporting member and spaced with each other in the direction of the circumference of a circle with
the center of which aligning with the axis of the
actuating rod, and
an electric circuit for selectively connecting
either one of the electromagnets with an electric
source, whereby said selected electromagnet
attracts the magnetizable member with the
actuating rod turning around the axis thereof.
2. A hydraulic damper substantially as
hereinbefore described, with reference to, and as
illustrated in, the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16878981U JPS5872546U (en) | 1981-11-12 | 1981-11-12 | Damping force adjustable hydraulic shock absorber |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB2112104A true GB2112104A (en) | 1983-07-13 |
Family
ID=15874495
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08232113A Withdrawn GB2112104A (en) | 1981-11-12 | 1982-11-10 | Adjusting hydraulic dampers |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS5872546U (en) |
| DE (1) | DE3241984A1 (en) |
| GB (1) | GB2112104A (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2153963A (en) * | 1983-12-21 | 1985-08-29 | Jidosha Denki Kogyo Kk | Hydraulic damper with adjustable flow path |
| WO1985004698A1 (en) * | 1984-04-04 | 1985-10-24 | Blixt, Rolf | Means for a shock-absorber |
| GB2158184A (en) * | 1984-05-03 | 1985-11-06 | Armstrong Patents Co Ltd | Hydraulic shock absorber with electromagnetically controlled valve |
| WO1986003565A1 (en) * | 1984-12-07 | 1986-06-19 | Magnus Lizell | A restriction valve device for hydraulic pressure fluids in vehicle shock absorbing mechanisms |
| GB2199699A (en) * | 1986-10-31 | 1988-07-13 | Atsugi Motor Parts Co Ltd | Rotary actuators for adjusting shock absorbers |
| US4923038A (en) | 1986-06-05 | 1990-05-08 | Lizell Magnus B | Method and apparatus for absorbing mechanical shock |
| US4943083A (en) * | 1989-03-13 | 1990-07-24 | Monroe Auto Equipment Company | Signal conditioning circuit assembly |
| US5123671A (en) * | 1989-03-13 | 1992-06-23 | Monroe Auto Equipment Company | Method and apparatus for controlling shock absorbers |
| US5152379A (en) * | 1990-04-16 | 1992-10-06 | Monroe Auto Equipment Company | Adjustable shock absorber assembly |
| US5217095A (en) | 1986-06-05 | 1993-06-08 | Monroe Auto Equipment Company | Method and apparatus for absorbing mechanical shock |
| US5326129A (en) * | 1984-04-04 | 1994-07-05 | Ohlins Racing Ab | Means for a shock absorber |
| US5529152A (en) * | 1994-07-08 | 1996-06-25 | Aimrite Systems International, Inc. | Variable constant force hydraulic components and systems |
Families Citing this family (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3324321C2 (en) * | 1983-04-11 | 1985-06-27 | F & O Electronic Systems GmbH & Co, 6901 Neckarsteinach | Adjustable valve for the piston rod of a vibration damper |
| DE3312899C2 (en) * | 1983-04-11 | 1985-06-13 | F & O Electronic Systems GmbH & Co, 6901 Neckarsteinach | Adjustable valve for the piston rod of a vibration damper |
| DE3323405A1 (en) * | 1983-06-29 | 1985-01-17 | Boge Gmbh, 5208 Eitorf | Hydraulic, adjustable shock absorber with a damping piston fixed to a hollow piston rod |
| DE3334255A1 (en) * | 1983-09-22 | 1985-04-11 | Boge Gmbh, 5208 Eitorf | Hydraulic, controllable shock absorber with a damping piston fixed on a hollow piston rod |
| ES533297A0 (en) * | 1983-06-29 | 1985-03-01 | Boge Gmbh | ADJUSTABLE HYDRAULIC DAMPER |
| JPS6052439U (en) * | 1983-09-20 | 1985-04-12 | トキコ株式会社 | Damping force adjustable hydraulic shock absorber |
| GB2147683B (en) * | 1983-09-24 | 1986-10-01 | Bilstein August Gmbh Co Kg | Shock absorber, with electromagnetically biased pressure responsive valve |
| DE3334704A1 (en) * | 1983-09-24 | 1985-04-11 | August Bilstein GmbH & Co KG, 5828 Ennepetal | Controllable shock absorber especially for motor vehicles |
| DE3348176C2 (en) * | 1983-09-24 | 1988-02-04 | August Bilstein Gmbh & Co Kg, 5828 Ennepetal, De | Adjustable shock absorber, in particular for motor vehicles |
| DE3344029C2 (en) * | 1983-12-06 | 1986-09-18 | Boge Gmbh, 5208 Eitorf | Hydraulic vibration damper |
| DE3419879C2 (en) * | 1984-05-28 | 1987-01-02 | Boge Gmbh, 5208 Eitorf | Hydraulic, adjustable twin-tube vibration damper |
| DE8421106U1 (en) * | 1984-06-09 | 1987-07-02 | Boge Gmbh, 5208 Eitorf | Adjustable hydraulic shock absorber |
| DE3421601A1 (en) * | 1984-06-09 | 1985-12-19 | Boge Gmbh, 5208 Eitorf | Adjustable hydraulic shock absorber |
| DE3432465A1 (en) * | 1984-09-04 | 1986-03-13 | Boge Gmbh, 5208 Eitorf | ADJUSTABLE DAMPING VALVE FOR A HYDRAULIC VIBRATION DAMPER |
| JPH0444905Y2 (en) * | 1984-10-19 | 1992-10-22 | ||
| NL8503031A (en) * | 1985-11-05 | 1987-06-01 | Koni Bv | ELECTRICALLY ADJUSTABLE SHOCK ABSORBER. |
| FR2605231B2 (en) * | 1985-12-04 | 1989-04-14 | Miccoli Cosimo | HYDRAULIC SYSTEM APPLIED TO WEIGHING EQUIPMENT |
| JPH0834683B2 (en) * | 1986-07-04 | 1996-03-29 | アイシン精機株式会社 | Rotary drive |
| JPH0732579B2 (en) * | 1986-10-31 | 1995-04-10 | 株式会社ユニシアジェックス | Variable damping force actuator for hydraulic shock absorber |
| JPH0732577B2 (en) * | 1987-10-22 | 1995-04-10 | アイシン精機株式会社 | Rotary actuator for multi-position control |
| JP2781176B2 (en) * | 1988-02-17 | 1998-07-30 | 株式会社ユニシアジェックス | Actuator |
| DE3805934A1 (en) * | 1988-02-25 | 1989-09-07 | Bosch Gmbh Robert | HYDRAULIC SHOCK ABSORBER |
-
1981
- 1981-11-12 JP JP16878981U patent/JPS5872546U/en active Granted
-
1982
- 1982-11-10 GB GB08232113A patent/GB2112104A/en not_active Withdrawn
- 1982-11-12 DE DE19823241984 patent/DE3241984A1/en not_active Ceased
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4645042A (en) * | 1983-12-21 | 1987-02-24 | Jidosha Denki Kogyo Kabushiki Kaisha | Hydraulic damper |
| GB2153963A (en) * | 1983-12-21 | 1985-08-29 | Jidosha Denki Kogyo Kk | Hydraulic damper with adjustable flow path |
| WO1985004698A1 (en) * | 1984-04-04 | 1985-10-24 | Blixt, Rolf | Means for a shock-absorber |
| US4732408A (en) * | 1984-04-04 | 1988-03-22 | Oehlin Kenth | Means for a shock-absorber |
| US5326129A (en) * | 1984-04-04 | 1994-07-05 | Ohlins Racing Ab | Means for a shock absorber |
| GB2158184A (en) * | 1984-05-03 | 1985-11-06 | Armstrong Patents Co Ltd | Hydraulic shock absorber with electromagnetically controlled valve |
| WO1986003565A1 (en) * | 1984-12-07 | 1986-06-19 | Magnus Lizell | A restriction valve device for hydraulic pressure fluids in vehicle shock absorbing mechanisms |
| US4597411A (en) * | 1984-12-07 | 1986-07-01 | Magnus Lizell | Restriction valve device for hydraulic pressure fluids in vehicle shock absorbing mechanisms |
| AU578785B2 (en) * | 1984-12-07 | 1988-11-03 | Magnus Lizell | A restriction valve device for hydraulic pressure fluids in vehicle shock absorbing mechanisms |
| US5025899A (en) | 1986-06-05 | 1991-06-25 | Lizell Magnus B | Method and apparatus for absorbing mechanical shock |
| US5217095A (en) | 1986-06-05 | 1993-06-08 | Monroe Auto Equipment Company | Method and apparatus for absorbing mechanical shock |
| US4923038A (en) | 1986-06-05 | 1990-05-08 | Lizell Magnus B | Method and apparatus for absorbing mechanical shock |
| GB2199699B (en) * | 1986-10-31 | 1990-03-28 | Atsugi Motor Parts Co Ltd | Rotary actuator |
| US5087868A (en) * | 1986-10-31 | 1992-02-11 | Atsugi Motor Parts Company, Ltd. | Rotary actuator |
| US4776437A (en) * | 1986-10-31 | 1988-10-11 | Atsugi Motor Parts Company, Limited | Variable damping force shock absorber with rotary actuator for rotary member |
| GB2199699A (en) * | 1986-10-31 | 1988-07-13 | Atsugi Motor Parts Co Ltd | Rotary actuators for adjusting shock absorbers |
| US4943083A (en) * | 1989-03-13 | 1990-07-24 | Monroe Auto Equipment Company | Signal conditioning circuit assembly |
| US5123671A (en) * | 1989-03-13 | 1992-06-23 | Monroe Auto Equipment Company | Method and apparatus for controlling shock absorbers |
| US5152379A (en) * | 1990-04-16 | 1992-10-06 | Monroe Auto Equipment Company | Adjustable shock absorber assembly |
| US5529152A (en) * | 1994-07-08 | 1996-06-25 | Aimrite Systems International, Inc. | Variable constant force hydraulic components and systems |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6224850Y2 (en) | 1987-06-25 |
| DE3241984A1 (en) | 1983-06-09 |
| JPS5872546U (en) | 1983-05-17 |
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| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |