CN102352870A - Adjustable-hydraulic-type energy accumulator for vehicles - Google Patents
Adjustable-hydraulic-type energy accumulator for vehicles Download PDFInfo
- Publication number
- CN102352870A CN102352870A CN201110292635XA CN201110292635A CN102352870A CN 102352870 A CN102352870 A CN 102352870A CN 201110292635X A CN201110292635X A CN 201110292635XA CN 201110292635 A CN201110292635 A CN 201110292635A CN 102352870 A CN102352870 A CN 102352870A
- Authority
- CN
- China
- Prior art keywords
- chamber
- piston
- cylinder body
- cylinder
- hydraulic
- 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.)
- Granted
Links
Images
Landscapes
- Actuator (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention relates to an adjustable-hydraulic-type energy accumulator which comprises a big hydraulic cylinder, a small hydraulic cylinder, a mass block and an adjustable mechanism. Two cavities in the big hydraulic cylinder are correspondingly communicated with two cavities in the small hydraulic cylinder; and the mass block is connected with the end part of a piston rod of the small hydraulic cylinder. When the external force is applied to the piston rod and cylinder body of the big hydraulic cylinder, a piston does straight-line motion relative to the cylinder body to push fluid to flow into the small hydraulic cylinder from the big hydraulic cylinder, so that a pressure difference is formed between two sides of the piston in the small hydraulic cylinder; the pressure difference drives the piston of the small hydraulic cylinder to move, and finally the mass block is driven to move. An electromagnetic directional valve in the adjustable mechanism is respectively connected with the big hydraulic cylinder and the small hydraulic cylinder; when a right electromagnet is electrified, the fluid is injected into the inner cavity of the hollow piston rod of the big hydraulic cylinder through a hydraulic fluid port E by virtue of a constant hydraulic pump, the speed of the mass block is changed and the energy accumulation of the energy accumulator is changed; and when a left electromagnet is electrified, the fluid is injected into the inner cavity of the hollow piston rod of the small hydraulic cylinder through a hydraulic fluid port F by virtue of the constant hydraulic pump, the speed of the mass block is changed and the energy accumulation of the energy accumulator is changed.
Description
Technical field
The present invention relates to a kind of hydraulic type accumulator, refer in particular to the adjustable hydraulic type accumulator of vehicle.
Background technique
Electromechanical integration has become an important development direction in new century engineering field.In this integrated process, often need will study as a big system after machinery and the electronics networking.In the tradition practical applications; There are two kinds of corresponding relations in machinery with electronics; A kind of is " power-voltage " correspondence; Be that quality, damping and spring are corresponding with inductance, resistance and electric capacity respectively; Another kind is " power-electric current " correspondence, and promptly quality, damping and spring are corresponding with electric capacity, resistance and inductance respectively.
Above-mentioned electric network element all has two independences, end points freely, and promptly two of inductance, resistance and electric capacity end points all are not subjected to the restriction of specified reference point.Yet mass elements but is not a real two-end-point element, and this is because an end points of quality is its barycenter, and another always links to each other with inertial reference frame, promptly mechanical ground connection.Therefore, in fact the electric capacity with an end ground connection is corresponding for mass elements.This has greatly limited freedom and flexibility ratio when people design Mechatronic Systems, and worse, the theoretical method with the research electric network of a large amount of electric network of accumulation for a long time can not be applied to the analysis and synthesis of mechanical network.Moreover, this undemanding correspondence has also limited the performance of passive mechanical network.Therefore, must find a kind of real two-end-point mechanical component to substitute mass elements.
Chinese patent 201010510953 discloses a kind of fluid power and has been used to case (claiming the hydraulic type accumulator again), is a kind of real two-end-point element as spring and this device of damper.Therefore, substitute the mass elements in the conventional mechanical system with this container of being used to, just strictness is corresponding gets up for machinery and electric network.Machinery with electric network strict corresponding after; A large amount of electric network theory and research methods just can be applied to mechanical system, comprise automobile suspension system, wheel steering system, train suspension system, building vibrating isolation system, helicopter vibrating isolation system, powered shock absorption device or the like.This fluid power is used to case and is comprised big oil hydraulic cylinder, small cylinder, mass block, high pressure hose A and high pressure hose B.Big oil hydraulic cylinder links to each other with small cylinder with high pressure hose B through high pressure hose A, and wherein big hydraulic cylinder piston is divided into two chambeies to cylinder body A, chamber A and chamber B, and piston rod stretches out from chamber one end of cylinder body.The small cylinder piston is divided into two chambeies to cylinder body B, chamber C and chamber D, and piston rod stretches out from chamber D one end of cylinder body.Mass block links to each other with the end of the piston rod B that stretches out small cylinder.After the connection, it is a chamber that the chamber A of big oil hydraulic cylinder and the chamber D of small cylinder just are communicated with, and it is a chamber that the chamber B of big oil hydraulic cylinder and the chamber C of small cylinder just are communicated with.When external force during along the piston rod that axially puts on big oil hydraulic cylinder of piston rod and cylinder body; Piston is done straight line motion with respect to cylinder body; Promote fluid and flow to small cylinder from big oil hydraulic cylinder; Make the piston both sides in the small cylinder form pressure reduction; The piston motion of pressure differential small cylinder finally drives the mass block motion.In fact, in movement process, piston will be done straight line motion with respect to oil hydraulic cylinder, and the hanger at big oil hydraulic cylinder two ends is exactly two end points that fluid power is used to case.The kinetic equations that fluid power is used to case does
, wherein
f,
aWith
bExpression is applied to the relative acceleration of power on the two-end-point, two-end-point and is used to hold coefficient (claiming scaling factor again) respectively, and being used to hold coefficient can be calculated with the ratio of the useful area of piston B by the quality of mass block and piston A.According to kinetic equations, quality and the piston A that changes mass block and the ratio of the useful area of piston B just can obtain having the suitable fluid power of being used to hold coefficient and be used to case.Fluid power is used to that case overcome can not strict corresponding shortcoming between machinery and the electric network.
Be used to case although designed fluid power, fluid power is used to the adjusting that case can not be realized the accumulator energy storage according to actual needs.
Therefore, press for a kind of adjustable hydraulic type accumulator on the engineering, can solve the hydraulic type accumulator and can not realize the problem that the accumulator energy storage is adjustable according to actual needs.
Summary of the invention
Technical problem to be solved by this invention is: overcome the shortcoming of said apparatus, provide a kind of adjustable hydraulic type accumulator to make it need realize that the accumulator energy storage is adjustable in the border factually.
The present invention solves this technical problem the technological scheme that is adopted: adjustable hydraulic type accumulator comprises big oil hydraulic cylinder, small cylinder, mass block and adjusting mechanism.Two chambeies in the big oil hydraulic cylinder are corresponding connections with two chambeies in the small cylinder, and mass block links to each other with the end of small cylinder piston rod.When external force during along the piston rod that axially puts on big oil hydraulic cylinder of piston rod and cylinder body; Piston is done straight line motion with respect to cylinder body; Promote fluid and flow to small cylinder from big oil hydraulic cylinder; Make the piston both sides in the small cylinder form pressure reduction; The piston motion of pressure differential small cylinder; The final mass block that drives moves, thus the characteristic that container is used in acquisition.Adjusting mechanism is connected with small cylinder with big oil hydraulic cylinder respectively through solenoid directional control valve; Solenoid directional control valve adopts the form of 3-position 4-way; When left and right sides electromagnet all during no electric circuit; Valve core of the electromagnetic valve is in meta; Big oil hydraulic cylinder and small cylinder box type piston bar inner chamber are communicated with, and this moment is quality of regulation piece store kinetic energy not; When right electromagnet was switched on, quantitative hydraulic pump injected big oil hydraulic cylinder box type piston bar inner chamber with fluid through hydraulic fluid port E by means of throttle valve, the mass block velocity variations, and the accumulator energy storage changes; When left electromagnet was switched on, quantitative hydraulic pump injected small cylinder box type piston bar inner chamber with fluid through hydraulic fluid port F by means of throttle valve, the mass block velocity variations, and the accumulator energy storage changes.
The concrete technological scheme of patent of the present invention is:
The present invention includes big oil hydraulic cylinder, small cylinder, high pressure hose A, high pressure hose B, mass block and adjusting mechanism.
Piston A during big oil hydraulic cylinder comprises cylinder body A and is placed on cylinder body A and the piston rod A that links to each other with piston A; Piston A divides coelosis A and chamber B cylinder body A; Be provided with a hydraulic fluid port A near cylinder body A end in the A of chamber; Be provided with a hydraulic fluid port B near cylinder body A end in the B of chamber; Piston rod A stretches out from chamber A one end of cylinder body A; The other end of piston rod A is enclosed within outside the box type piston bar C; The other end of box type piston bar C passes from piston A center; And stretch out from the chamber B of cylinder body A; Cylinder body A upper end is provided with a hydraulic fluid port E, links to each other with the solenoid directional control valve working oil chamber E of adjusting mechanism.
Piston B during small cylinder comprises cylinder body B and is placed on cylinder body B and the piston rod B that links to each other with piston B; Piston B divides coelosis C and chamber D cylinder body B; Be provided with a hydraulic fluid port C near cylinder body B end in the C of chamber; Be provided with a hydraulic fluid port D near cylinder body B end in the D of chamber; Piston rod B stretches out from chamber D one end of cylinder body B; The other end of piston rod B is enclosed within outside the box type piston bar D; The other end of box type piston bar D passes from piston B center; And stretch out from the chamber C of cylinder body B; Cylinder body B lower end is provided with a hydraulic fluid port F, links to each other with the solenoid directional control valve working oil chamber F of adjusting mechanism.
The two ends of high pressure hose A are connected with hydraulic fluid port D with hydraulic fluid port A respectively; The two ends of high pressure hose B are connected with hydraulic fluid port C with hydraulic fluid port B respectively; After the connection; It is a chamber that the chamber A of big oil hydraulic cylinder and the chamber D of small cylinder just are communicated with; It is a chamber that the chamber B of big oil hydraulic cylinder and the chamber C of small cylinder just are communicated with, and all is full of fluid in two chambeies.
The ratio of the useful area of chamber A and chamber D inner carrier A and piston B (it is long-pending that piston area deducts the cross sections of piston rod) equals the ratio of chamber B and chamber C inner carrier A and the area of piston B.In order to guarantee that the present invention has enough big scaling factor, the ratio of chamber A and chamber D inner carrier A and the useful area of piston B should greater than.
Mass block links to each other with the end of the piston rod B that stretches out small cylinder.
Adjusting mechanism comprises solenoid directional control valve and the throttle valve that links to each other with solenoid directional control valve and quantitative hydraulic pump that links to each other with throttle valve and relief valve; Also has the fuel tank that links to each other with relief valve with quantitative hydraulic pump; The working oil chamber E of solenoid directional control valve links to each other with the hydraulic fluid port E of big oil hydraulic cylinder; The working oil chamber F of solenoid directional control valve links to each other with the hydraulic fluid port F of small cylinder; Solenoid directional control valve oil suction chamber P links to each other with an end of throttle valve; The other end of throttle valve links to each other with relief valve with quantitative hydraulic pump; The other end of quantitative hydraulic pump links to each other with fuel tank, and the other end of relief valve links to each other with fuel tank.
Description of drawings
Fig. 1 is a hydraulic type accumulator schematic representation.
Fig. 2 is the adjusting mechanism schematic representation.
Among the figure, A 7-piston A 8-chamber, the big oil hydraulic cylinder 2-of 1-cylinder body A 3-hydraulic fluid port A 4-piston rod A 5-piston rod C 6-chamber B 9-fluid 10-hydraulic fluid port B 11-high pressure hose B 12-mass block 13-small cylinder 14-high pressure hose A 15-hydraulic fluid port D 16-cylinder body B 17-piston rod B 18-piston rod D 19-chamber D 20-piston B 21-chamber C 22-hydraulic fluid port C
23-adjusting mechanism 24-fuel tank 25-relief valve 26-solenoid directional control valve 27-throttle valve 28-quantitative hydraulic pump.
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is described further.
The present invention includes big oil hydraulic cylinder 1, small cylinder 13, high pressure hose A14, high pressure hose B11, mass block 12 and adjusting mechanism 23.
Piston A7 during big hydraulic cylinder 1 comprises cylinder body A2 and is placed on cylinder body A2 and the piston rod A4 that links to each other with piston A7; Piston A7 divides coelosis A6 and chamber B8 cylinder body A2; Be provided with a hydraulic fluid port A3 near cylinder body A2 end in the A6 of chamber; Be provided with a hydraulic fluid port B10 near cylinder body A2 end in the B8 of chamber; Piston rod A4 stretches out from chamber A6 one end of cylinder body A2; The other end of piston rod A4 is enclosed within outside the hollow piston bar C5; The other end of hollow piston bar C5 passes from piston A7 center; And stretch out from the chamber B8 of cylinder body A2; Cylinder body A2 upper end is provided with a hydraulic fluid port E, links to each other with the solenoid directional control valve 26 working oil chamber E of adjustable mechanism 23.
Piston B20 during small cylinder 13 comprises cylinder body B16 and is placed on cylinder body B16 and the piston rod B17 that links to each other with piston B20; Piston B20 divides coelosis C21 and chamber D19 cylinder body B16; Be provided with a hydraulic fluid port C22 near cylinder body B16 end in the C21 of chamber; Be provided with a hydraulic fluid port D15 near cylinder body B16 end in the D19 of chamber; Piston rod B17 stretches out from chamber D19 one end of cylinder body B16; The other end of piston rod B17 is enclosed within outside the hollow piston bar D18; The other end of hollow piston bar D18 passes from piston B20 center; And stretch out from the chamber C21 of cylinder body B16; Cylinder body B16 lower end is provided with a hydraulic fluid port F, links to each other with the solenoid directional control valve 26 working oil chamber F of adjustable mechanism 23.
The two ends of high pressure hose A14 are connected with hydraulic fluid port D15 with hydraulic fluid port A3 respectively; The two ends of high pressure hose B11 are connected with hydraulic fluid port C22 with hydraulic fluid port B10 respectively; After the connection; It is a chamber that the chamber A6 of big oil hydraulic cylinder 1 and the chamber D19 of small cylinder 13 just are communicated with; It is a chamber that the chamber B8 of big oil hydraulic cylinder 1 and the chamber C21 of small cylinder 13 just are communicated with, and all is full of fluid 9 in two chambeies.
The ratio of the useful area of chamber A6 and chamber D19 inner carrier A7 and piston B20 (it is long-pending that piston area deducts the cross sections of piston rod) equals the ratio of chamber B8 and chamber C21 inner carrier A7 and the area of piston B20.In order to guarantee that the present invention has enough big scaling factor, chamber A6 and chamber D19 inner carrier A7 should be greater than 3 with the ratio of the useful area of piston B20.
Mass block 12 links to each other with the end of the piston rod B17 that stretches out small cylinder 13.
Quantitative hydraulic pump 28 and overflow valve 25 that adjustable mechanism 23 comprises solenoid directional control valve 26 and the choke valve 27 that links to each other with solenoid directional control valve 26 and links to each other with choke valve 27; Also has the fuel tank 24 that links to each other with overflow valve 25 with quantitative hydraulic pump 28; The working oil chamber E of solenoid directional control valve 26 links to each other with the hydraulic fluid port E of big hydraulic cylinder 1; The working oil chamber F of solenoid directional control valve 26 links to each other with the hydraulic fluid port F of small cylinder 13; Solenoid directional control valve 26 oil suction chamber P link to each other with an end of choke valve 27; The other end of choke valve 27 links to each other with overflow valve 25 with quantitative hydraulic pump 28; The other end of quantitative hydraulic pump 28 links to each other with fuel tank 24, and the other end of overflow valve 25 links to each other with fuel tank 24.
Below in conjunction with accompanying drawing practical implementation process of the present invention is described further.
Shown in Figure 1, when an external force such a large reverse
f ?, In the axial direction is applied to the piston rod and the cylinder block A2, A4, A4 promote the large cylinder piston rod 1 the piston relative to the cylinder block A2 A7 linear motion, the oil chamber through the high-pressure hose B8 B11 B8 flow from the chamber cavity C21, C21 chamber cavity B8 and increased pressure within the fluid pressure zone is formed, while the oil chamber D19 fluid from the chamber through the hydraulic hoses A14 D19 flow chamber A6, A6 cavity D19 and the cavity is formed within the low pressure fluid pressure reduction zone, and then formed on both sides of the differential piston B20, B20 with the pressure driving the piston rod along the B17 D19 cavity side movement, and ultimately driving mass 12 movement.The result is, external force promotes mass blockes 12 motions through big oil hydraulic cylinder 1 and small cylinder 13, thereby obtained the characteristic of accumulator, and in fact, the hydraulic type accumulator is exactly through two oil hydraulic cylinders the inertia of mass block 12 have been encapsulated.When if external force puts on piston rod A4 and cylinder body A2 with opposite direction, piston B20 is with opposite direction motion, and promptly this is an opposite process.Solenoid directional control valve 26 in the adjusting mechanism 23 is connected with small cylinder 13 with big oil hydraulic cylinder 1 respectively; The form that solenoid directional control valve 26 adopts 3-position 4-way; When left and right sides electromagnet all during no electric circuit; Valve core of the electromagnetic valve is in meta; Big oil hydraulic cylinder 1 is communicated with small cylinder 13 box type piston bar inner chambers, and this moment is the store kinetic energy of quality of regulation piece 12 not; When right electromagnet was switched on, quantitative hydraulic pump 28 injected big oil hydraulic cylinder 1 box type piston bar C5 inner chamber with fluid through hydraulic fluid port E by means of throttle valve 27, mass block 12 velocity variations, and the accumulator energy storage changes; When left electromagnet was switched on, quantitative hydraulic pump 28 injected small cylinder box type piston bar D18 inner chamber with fluid through hydraulic fluid port F by means of throttle valve 27, mass block 12 velocity variations, and the accumulator energy storage changes.
Below in conjunction with accompanying drawing characteristics of the present invention are further specified.
As spring, damper and electric capacity, resistance and inductance; Accumulator also is a kind of ideal element; When therefore actual device being abstracted into accumulator; Must neglect some less important factors; Such as less sliding friction; Also have as desirable hydraulic damper, ignore the quality of piston, piston rod, piston cylinder and fluid, will do the idealized processing of ignoring secondary cause for the present invention equally.
To energy-storage travelling wave tube, the power of input element equates with the element power absorbed, can get hydraulic type accumulator scaling factor in view of the above and do
……………………(1)
Wherein, the gross mass of piston rod B17, piston B20 and mass block 12 does
m, piston A7 and piston B20 useful area are respectively
S R With
S r
According to formula (1), the useful area of quality and piston A7 and piston B20 that can be through adjustment mass block 12 recently design a hydraulic type accumulator with required scaling factor.Can know by formula (1), even 12 given less quality of quality also can obtain bigger scaling factor.
Put on big oil hydraulic cylinder two ends, the power of opposite sign but equal magnitude
fBe directly proportional with the relative acceleration of crossing over the element two ends:
The energy of storing in the accumulator is so:
Where,
,
is the velocity across the element, b is the proportional coefficient accumulator.
As shown in Figure 2; Solenoid directional control valve 26 in the adjusting mechanism 23 is connected with small cylinder 13 with big oil hydraulic cylinder 1 respectively; Quantitative hydraulic pump 28 is regulated the flow that gets into box type piston bar (C or D) inner chamber by means of throttle valve 27; When box type piston bar (C or D) inner chamber fuel delivery needs above it; Unnecessary fluid flows back to fuel tank 24 from relief valve 25, keeps system's (hydraulic pressure delivery side of pump) constant pressure simultaneously again.
Wherein, k is by the section configuration of restriction and the coefficient of size and the decision of fluid character; N is by the index of restriction shape decision, generally in 0.5 ~ 1 scope, when being similar to the thin-walled hole, approaches 0.5, when being similar to elongated hole, approaches 1; A is the flow area of restriction.
The form that solenoid directional control valve 26 adopts 3-position 4-way, " Y " type meta function.When left and right sides electromagnet all during no electric circuit, valve core of the electromagnetic valve is in meta, and box type piston bar inner chamber is communicated with, and this moment is the store kinetic energy of quality of regulation piece 12 not.
When right electromagnet was switched on, quantitative hydraulic pump 28 injected big oil hydraulic cylinder box type piston bar C5 inner chamber by means of throttle valve 27 fluid through hydraulic fluid port E, mass block 12 velocity variations, and the accumulator energy storage changes.The speed that changes is:
……………………(5)
Wherein, Q is the flow through throttle valve, A
RUseful area for big oil hydraulic cylinder box type piston bar C5 inner chamber.
When left electromagnet was switched on, quantitative hydraulic pump 28 injected small cylinder box type piston bar D18 inner chamber with fluid through hydraulic fluid port F by means of throttle valve 27, mass block 12 velocity variations, and the accumulator energy storage changes.The speed that changes is:
……………………(6)
Wherein, Q is the flow through throttle valve, A
rUseful area for small cylinder box type piston bar D18 inner chamber.
Can know being changed to of accumulator stored energy by formula (2)～(6):
Claims (3)
1. an adjustable hydraulic type accumulator is characterized in that, comprises big oil hydraulic cylinder (1), small cylinder (13), high pressure hose A (14), high pressure hose B (11), mass block (12) and adjusting mechanism (23);
Big hydraulic cylinder (1) comprises cylinder body A(2) be placed on cylinder body A(2) in piston A(7) and with piston A(7) the piston rod A(4 that links to each other); Piston A(7) cylinder body A(2) branch coelosis A(6) and chamber B(8); Chamber A(6) close cylinder body A(2 in) end is provided with a hydraulic fluid port A(3); Chamber B(8) close cylinder body A(2 in) end is provided with a hydraulic fluid port B(10); Piston rod A(4) from cylinder body A(2) chamber A(6) end stretches out; Piston rod A(4) the other end is enclosed within hollow piston bar C(5) outside; Hollow piston bar C(5) the other end is from piston A(7) center passes; And from cylinder body A(2) chamber B(8) stretch out; Cylinder body A(2) upper end is provided with a hydraulic fluid port E, links to each other with solenoid directional control valve (26) the working oil chamber E of adjustable mechanism (23);
Small cylinder (13) comprises cylinder body B(16) be placed on cylinder body B(16) in piston B(20) and with piston B(20) the piston rod B(17 that links to each other); Piston B(20) cylinder body B(16) branch coelosis C(21) and chamber D(19); Chamber C(21) close cylinder body B(16 in) end is provided with a hydraulic fluid port C(22); Chamber D(19) close cylinder body B(16 in) end is provided with a hydraulic fluid port D(15); Piston rod B(17) from cylinder body B(16) chamber D(19) end stretches out; Piston rod B(17) the other end is enclosed within hollow piston bar D(18) outside; Hollow piston bar D(18) the other end is from piston B(20) center passes; And from cylinder body B(16) chamber C(21) stretch out; Cylinder body B(16) lower end is provided with a hydraulic fluid port F, links to each other with solenoid directional control valve (26) the working oil chamber F of adjustable mechanism (23);
The two ends of high pressure hose A (14) are connected with hydraulic fluid port D (15) with hydraulic fluid port A (3) respectively; The two ends of high pressure hose B (11) are connected with hydraulic fluid port C (22) with hydraulic fluid port B (10) respectively; After the connection; It is a chamber that the chamber A (6) of big oil hydraulic cylinder (1) and the chamber D (19) of small cylinder (13) just are communicated with; It is a chamber that the chamber B (8) of big oil hydraulic cylinder (1) and the chamber C (21) of small cylinder (13) just are communicated with, and all is full of fluid (9) in two chambeies;
Mass block (12) links to each other with the end of the piston rod B (17) that stretches out small cylinder (13);
Adjustable mechanism (23) comprises solenoid directional control valve (26) and the choke valve (27) that links to each other with solenoid directional control valve (26) and quantitative hydraulic pump (28) that links to each other with choke valve (27) and overflow valve (25); Also has the fuel tank (24) that links to each other with overflow valve (25) with quantitative hydraulic pump (28); The working oil chamber E of solenoid directional control valve (26) links to each other with the hydraulic fluid port E of big hydraulic cylinder (1); The working oil chamber F of solenoid directional control valve (26) links to each other with the hydraulic fluid port F of small cylinder (13); Solenoid directional control valve (26) oil suction chamber P links to each other with an end of choke valve (27); The other end of choke valve (27) links to each other with overflow valve (25) with quantitative hydraulic pump (28); The other end of quantitative hydraulic pump (28) links to each other with fuel tank (24), and the other end of overflow valve (25) links to each other with fuel tank (24).
2. adjustable hydraulic type accumulator according to claim 1 is characterized in that, the ratio of the useful area of said chamber A (6) and chamber D (19) inner carrier A (7) and piston B (20) is greater than 3.
3. adjustable hydraulic type accumulator according to claim 1; It is characterized in that said solenoid directional control valve (26) adopts the form of 3-position 4-way, the centre is oil suction chamber P; That be adjacent is working oil chamber E and working oil chamber F, the oil back chamber T that two ends interconnect in addition; When the two ends electromagnet all cut off the power supply, spool mediated, and working oil chamber E and working oil chamber F are communicated with; When the right-hand member electromagnet is switched on, its armature will promote spool through push rod and be moved to the left, and oil suction chamber P and working oil chamber E communicate, and working oil chamber F and oil back chamber T communicate; When the left end electromagnet is switched on, its armature will promote spool through push rod and move right, and oil suction chamber P and working oil chamber F are communicated with, and working oil chamber E and oil back chamber T are communicated with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110292635.XA CN102352870B (en) | 2011-09-30 | 2011-09-30 | Adjustable-hydraulic-type energy accumulator for vehicles |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110292635.XA CN102352870B (en) | 2011-09-30 | 2011-09-30 | Adjustable-hydraulic-type energy accumulator for vehicles |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102352870A true CN102352870A (en) | 2012-02-15 |
| CN102352870B CN102352870B (en) | 2014-04-09 |
Family
ID=45576499
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110292635.XA Expired - Fee Related CN102352870B (en) | 2011-09-30 | 2011-09-30 | Adjustable-hydraulic-type energy accumulator for vehicles |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102352870B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108105170A (en) * | 2017-12-31 | 2018-06-01 | 赵德朝 | A kind of dedicated piston accumulator of hydraulic breaking hammer |
| CN108956069A (en) * | 2018-06-15 | 2018-12-07 | 江苏大学 | A kind of electromechanical used container Mechanics Performance Testing operating condition design method |
| CN109281896A (en) * | 2018-11-29 | 2019-01-29 | 山海特种装备股份有限公司 | A kind of fluid pressure drive device and packaging cargo loading machine |
| CN113719572A (en) * | 2021-08-03 | 2021-11-30 | 中国北方车辆研究所 | Double-cylinder fluid inerter |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1060326A (en) * | 1990-09-25 | 1992-04-15 | 哈尔滨建筑工程学院 | Hydraulic-mass vibration control system |
| JPH0658303A (en) * | 1991-10-12 | 1994-03-01 | Mercedes Benz Ag | Device for controlling supply of liquid to hydraulic type assembly |
| CN101975200A (en) * | 2010-10-19 | 2011-02-16 | 江苏大学 | Hydraulic inert container device |
| US20110061375A1 (en) * | 2004-12-01 | 2011-03-17 | George Kadlicko | Hydraulic Drive System |
-
2011
- 2011-09-30 CN CN201110292635.XA patent/CN102352870B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1060326A (en) * | 1990-09-25 | 1992-04-15 | 哈尔滨建筑工程学院 | Hydraulic-mass vibration control system |
| JPH0658303A (en) * | 1991-10-12 | 1994-03-01 | Mercedes Benz Ag | Device for controlling supply of liquid to hydraulic type assembly |
| US20110061375A1 (en) * | 2004-12-01 | 2011-03-17 | George Kadlicko | Hydraulic Drive System |
| CN101975200A (en) * | 2010-10-19 | 2011-02-16 | 江苏大学 | Hydraulic inert container device |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108105170A (en) * | 2017-12-31 | 2018-06-01 | 赵德朝 | A kind of dedicated piston accumulator of hydraulic breaking hammer |
| CN108956069A (en) * | 2018-06-15 | 2018-12-07 | 江苏大学 | A kind of electromechanical used container Mechanics Performance Testing operating condition design method |
| CN108956069B (en) * | 2018-06-15 | 2020-03-31 | 江苏大学 | Mechanical property test working condition design method for electromechanical inerter |
| CN109281896A (en) * | 2018-11-29 | 2019-01-29 | 山海特种装备股份有限公司 | A kind of fluid pressure drive device and packaging cargo loading machine |
| CN113719572A (en) * | 2021-08-03 | 2021-11-30 | 中国北方车辆研究所 | Double-cylinder fluid inerter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102352870B (en) | 2014-04-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103889747B (en) | Collection of energy is passive and Active suspension | |
| CN106678256B (en) | A kind of electric vehicle magneto-electric self-powered suspension damper | |
| CN205244233U (en) | From energizing quantity formula vehicle magnetorheological damper device | |
| CN1781748B (en) | Vehicle suspension system | |
| CN101435448B (en) | Combined actuator with rheological control brake | |
| CN103644248B (en) | Controlled used appearance and the magnetorheological used case of damping and controlling method thereof | |
| CN100364792C (en) | Vehicle hydraulic damper with actively adjustable damping for semiactive suspension | |
| CN105276060B (en) | A kind of dual circuit liquid of variable used matter coefficient is used to container | |
| CN102352870B (en) | Adjustable-hydraulic-type energy accumulator for vehicles | |
| CN103423364A (en) | Hydraulic damper with adjustable damping | |
| US10052926B2 (en) | Regenerative hydraulic shock-absorber for vehicle suspension | |
| CN102619921A (en) | Shock absorber device with shunt-wound inertial container and damping | |
| CN102494080A (en) | Integral shock absorber device of inertial container and damper in coaxial parallel connection | |
| CN101975200B (en) | Hydraulic inert container device | |
| CN202971728U (en) | Integrated shock absorber provided with coaxially tandem inertial container and damping elements | |
| CN111089135B (en) | Electromagnetic type is used to hold device | |
| CN103423363A (en) | Hydraulic damper with actively-adjustable damping | |
| CN103603914B (en) | Magnetostriction damper | |
| CN202883876U (en) | Integrated absorber device | |
| CN206344652U (en) | A kind of hydro-pneumatic suspension system of achievable active and half active switching control | |
| CN202991714U (en) | Inertia coefficient-adjustable vehicle hydraulic inert container device | |
| CN104565178A (en) | Hydraulic shock absorber with active adjustable damping | |
| CN202228470U (en) | Magneto-rheological fluid gas-liquid damping cylinder | |
| CN203223265U (en) | Overflow valve and actuator | |
| CN102352908B (en) | Motorcycle automatic damping-changing front shock absorber damper |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP02 | Change in the address of a patent holder |
Address after: 225814, Jiangsu County, Yangzhou City, Sheyang province Baoying Lake Town Industrial Concentration Area Patentee after: Jiangsu University Address before: Zhenjiang City, Jiangsu Province, 212013 Jingkou District Road No. 301 Patentee before: Jiangsu University |
|
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140409 Termination date: 20160930 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |