CN1594897A - Self-protection large gear ratio hydraulic cylinder - Google Patents
Self-protection large gear ratio hydraulic cylinder Download PDFInfo
- Publication number
- CN1594897A CN1594897A CN 200410009276 CN200410009276A CN1594897A CN 1594897 A CN1594897 A CN 1594897A CN 200410009276 CN200410009276 CN 200410009276 CN 200410009276 A CN200410009276 A CN 200410009276A CN 1594897 A CN1594897 A CN 1594897A
- Authority
- CN
- China
- Prior art keywords
- chamber
- oil
- valve
- hydraulic cylinder
- speed ratio
- 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
Landscapes
- Actuator (AREA)
Abstract
This invention provides a hydraulic cylinder of self-protection and high speed ratio and its facture. This cylinder includes: hydraulic pump and hydraulic cylinder, commutating valve, bidirectional hydraulic lock, hydraulic cylinder with space A and space B, the hydraulic pump is linked to the space A orderly through the commutating valve and the lock, the space B is connected to the cylinder orderly through the bidirectional lock and the valve; and in the hydraulic cylinder and between the space A and B there is overflow valve. When the pressure of space B is higher than that of space A and reaches the safety pressure of the cylinder, the oil of space B will flow to space A through the overflow valve. The project will not increase the complexity of the whole system, and will not influent the outer framework of the cylinder, and is very convenient to be used with the present equipment.
Description
Technical field
The present invention relates to a kind of hydraulic jack, relate in particular to a kind of large speed ratio hydraulic jack that has the self-protecting device structure.
Background technique
When giving the double-acting hydraulic cylinder fuel feeding with quantitative hydraulic pump, the to-and-fro motion speed of oil hydraulic cylinder is unequal.The ratio of the to-and-fro motion speed of oil hydraulic cylinder can be tried to achieve by the rodless cavity sectional area of two-way ram cylinder and the ratio of rod chamber sectional area.If the speed ratio of oil hydraulic cylinder is i, the rodless cavity sectional area is S
A, rod chamber sectional area S
B, the hydraulic cylinder piston rod speed of stretching out is V
1, the hydraulic cylinder piston rod speed of returning is V
2, then have:
i＝V
2/V
1＝S
A/S
B
The speed ratio i of general oil cylinder is not more than 2, but at some special occasions, improve the strut stability of piston rod and oil hydraulic cylinder diameter or weight when being restricted and requiring thrust as hope much larger than pulling force, having to improve the speed ratio of oil hydraulic cylinder, is exactly typical example as the telescopic hydraulic cylinder and the vertical hydraulic cylinder of truck crane.Yet rod chamber cylinder barrel the diameter big or diastrophic phenomenon that rises but often appears in this large speed ratio oil hydraulic cylinder, causes scrapping of oil hydraulic cylinder.
Fig. 1 is the hydraulic control circuit schematic diagram of truck crane vertical hydraulic cylinder.Its vertical hydraulic cylinder is typical large speed ratio oil hydraulic cylinder, and speed ratio is generally i=2.5～5.
Oil hydraulic pump 1 extracts hydraulic oil from fuel tank 5, pull the Joystick of selector valve 2, make the A mouth oil-feed of bidirectional hydraulic lock 3, pressure oil is just opened the one-way valve on the left side, enter the rodless cavity (A chamber) of vertical hydraulic cylinder 4 from the AA mouth, open the one-way valve on the right simultaneously by the control oil channel of bidirectional hydraulic lock inside, make the hydraulic oil of the rod chamber (B chamber) of vertical hydraulic cylinder 4 get back to fuel tank 5 by this one-way valve and selector valve, the piston rod of vertical hydraulic cylinder stretches out.The selector valve Joystick is pulled meta in good time, the bidirectional hydraulic lock locking, piston rod can be parked in the position that needs.When the needs piston rod bounces back, oppositely pull the Joystick of selector valve 2, make the oil-feed of bidirectional hydraulic lock B mouth, pressure oil is just opened the one-way valve on the right, enter vertical hydraulic cylinder rod chamber from the BB mouth, open the one-way valve on the left side simultaneously by the control oil channel of bidirectional hydraulic lock inside, make the oil of vertical hydraulic cylinder rodless cavity get back to fuel tank, the piston rod withdrawal of vertical hydraulic cylinder by this one-way valve and selector valve.
In the prior art, this large speed ratio oil hydraulic cylinder usually at the cylinder barrel of rod chamber one side because the cylinder failure phenomenon that rises that superpressure causes.The reason that this large speed ratio oil hydraulic cylinder cylinder barrel distortion is scrapped is the high pressure owing to the B chamber, and this high pressure is the inoperative high pressure, and how eliminating this high pressure is the key of dealing with problems
The 4th of " hydropneumatic and the sealing " of publishing in August, 2002 interimly discloses one piece " research of self-protection large speed ratio cylinder design "; analyzed large speed ratio oil hydraulic cylinder failure reasons; and provide a kind of self-protection large speed ratio oil hydraulic cylinder; it leaks into fuel tank with the high pressure oil in B chamber through relief valve by exterior line; solve the problem that oil hydraulic cylinder lost efficacy; but this scheme; can make on the one hand whole hydraulic system become complicated, on the other hand even can limit and to implement because of the oil hydraulic cylinder space outerpace.
Summary of the invention
Technical problem to be solved by this invention provides a kind of large speed ratio hydraulic jack that has self-protecting device; it does not only increase the complexity of whole hydraulic system; and can not influence oil hydraulic cylinder space outerpace structure, this scheme can be implemented on existing equipment very easily.
To achieve these goals, the invention provides a kind of self-protection large speed ratio oil hydraulic cylinder and manufacture method thereof, this oil hydraulic cylinder comprises: oil hydraulic pump and hydraulic oil container, selector valve, bidirectional hydraulic lock, have the double-act-ing hydraulic J-Horner in A chamber and B chamber, described oil hydraulic pump is connected to the A chamber of described double-act-ing hydraulic J-Horner successively by selector valve and bidirectional hydraulic lock, the B chamber of described double-act-ing hydraulic J-Horner is connected to hydraulic oil container by bidirectional hydraulic lock, selector valve successively; Wherein, in the inside of described double-act-ing hydraulic J-Horner, also be provided with a relief valve between described A chamber and the B chamber.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder, wherein, described relief valve is fixedly installed on the head of described piston rod.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder; wherein; the head of described piston rod offers a descending step type inner chamber; adopt the relief valve of plug-in type structure to be fixed in the described step type inner chamber; the opening end of described step type inner chamber is communicated with described A chamber, and the top of described step type inner chamber is communicated with described B chamber.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder; wherein; described piston rod comprises the piston body of rod, piston bushing, a plurality of seal ring again; described piston bushing is fixed on the end of the described piston body of rod; described seal ring fixed cover on the described piston bushing and and described hydraulic jack inboard wall of cylinder block between form sealing configuration, be provided with sealing configuration between the described piston body of rod and the described piston bushing.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder; wherein; described plug-in type relief valve comprises again: locking nut; Sealing; regulate bolt; spring; valve body; spool; described valve body is the tubular cavity; have valve opening in the middle of the tubular cavity bottom; tubular cavity bottom sidewall has draining hole and equalizing orifice; described spring; valve body and spool are arranged in the described tubular cavity; described adjusting bolt and described cavity inner wall are screw thread and revolve and be connected and by black box sealing; the awl point of described spool inserts in the described valve opening; the two ends of described spring are separately positioned in the groove of described adjusting bolt and spool; described locking nut is arranged in described adjusting bolt and stretches out on the end of described valve body and withstand described valve body; the chamber, front and back that draining hole that is communicated with described A chamber and equalizing orifice are communicated with described spool respectively; described valve opening is communicated with described B chamber; the awl point of described spool can be in described A chamber; in described valve opening, move the formation valve body under the pressure effect in spring force and B chamber and open/close state, on the outer side wall between described tubular cavity bottom draining hole and the valve opening, also be with another Sealing.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder; wherein; described piston rod also comprises another set of piston sleeve on described piston rod; described piston rod head is gradually wide stepped of external diameter; described piston bushing and piston sleeve inboard are equipped with and the corresponding step in the described piston rod head outside; described piston bushing is axially fixed in described piston sleeve on the described piston rod, has the oil guiding hole that is communicated with described B chamber and valve opening respectively on the described piston sleeve.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder; wherein; described plug-in type relief valve also comprises a valve bonnet; described valve bonnet is provided with a containing space; the end that described locking nut and adjusting bolt stretch out described valve body is contained in the described containing space; the opening of described valve bonnet is extended with bending edge, and described bending edge is stuck in the groove between described locking nut and the described valve body.
Above-mentioned large speed ratio oil hydraulic cylinder, wherein, the termination portion that described adjusting bolt stretches out described valve body one end also has to regulate revolves the hole.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder, wherein, described relief valve spiral is connected on the interior cavity wall of described step type.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder wherein, also offers the screw thread that is connected with cavity wall in the described step type on the described valve outer wall.
In order to realize above-mentioned purpose better, the present invention also provides a kind of manufacture method of self-protection large speed ratio hydraulic jack, comprises the steps:
One oil hydraulic pump and hydraulic oil container are set, are used to provide and reclaim high-pressure and hydraulic oil;
One selector valve is set, is used for switching as required the oil circuit direction;
One two-way hydraulic lock is set, is used for the locking oil circuit, prevent that the oil cylinder piston bar from freely stretching;
One double-act-ing hydraulic J-Horner that has A chamber and a B chamber is set, is used for moving by promoting oil cylinder at A chamber and B chamber I/O hydraulic oil;
Wherein, in the inside of described double-act-ing hydraulic J-Horner, between described A chamber and the B chamber relief valve is set, when the B cavity pressure was higher than the A chamber and reach oil hydraulic cylinder security settings pressure, the high pressure oil in described B chamber leaked into described A chamber through described relief valve; Described security settings pressure is that hydraulic jack does not take place to be out of shape the safety pressure that lost efficacy because of cylinder barrel.
The manufacture method of above-mentioned self-protection large speed ratio hydraulic system, wherein, the oil pressure relief of described relief valve is adjustable.
Above-mentioned self-protection large speed ratio oil hydraulic cylinder, wherein, the overflow set pressure of described relief valve can be undertaken by following formula:
p＝(1-1/i)p
B
Wherein, p
BB cavity pressure when just having begun overflow for relief valve, p
B=2 δ σ
b/ D
1/ n;
The oil hydraulic cylinder internal diameter of cylinder is D
1, the wall thickness of cylinder barrel thinnest part is δ, Tensile strength is σ
b, safety coefficient is n, i is a speed ratio.
Adopt such scheme, install the relief valve in a B chamber to A chamber additional between A, B chamber, when the B cavity pressure was higher than the A chamber and reach oil hydraulic cylinder security settings pressure, then B-A was communicated with pressure release, and after high pressure released, relief valve recovered blocking again.The oil pressure relief of relief valve configures in advance, can not change because of the A cavity pressure; Relief valve and large speed ratio oil hydraulic cylinder have just been formed the large speed ratio oil hydraulic cylinder with protective function like this.Installed the large speed ratio oil hydraulic cylinder of relief valve additional; not only can guarantee when the very big unexpected off-load of thrust load, the protection oil hydraulic cylinder rod chamber cylinder that can superpressure do not rise, and can also guarantee under any circumstance; hydraulic lock can both normally be opened, thereby has realized the reliably working of large speed ratio oil hydraulic cylinder.
Further specify specific embodiments of the invention below in conjunction with accompanying drawing.
Description of drawings
Fig. 1 is the existing working principle schematic representation that is used for the large speed ratio oil hydraulic cylinder on the truck crane;
Fig. 2 adopts the work schematic representation of the large speed ratio oil hydraulic cylinder of self-protection structure for the present invention;
Fig. 3 is a kind of large speed ratio hydraulic cylinder structure that has self-protection structure shown in the present;
Fig. 4 is the plug-in type structure of relief valve in the large speed ratio oil hydraulic cylinder shown in Figure 3.
Wherein, reference character:
The 1-oil hydraulic pump, 2-selector valve, 3-bidirectional hydraulic lock;
The 4-double-act-ing hydraulic J-Horner, 41-A chamber, 42-B chamber, 43-inboard wall of cylinder block;
The 5-fuel tank;
The 6-piston rod, 61-piston bushing, 62, the 64-seal ring, 63-piston sleeve, 631-oil guiding hole, the top of 65-inner chamber, 66-lumen openings end, 661-draining road;
The 7-relief valve;
The 71-valve bonnet, 711-containing space, 712-bending edge;
The 72-locking nut;
73,78-Sealing;
74-regulates bolt, and 741-regulates and revolves the hole, and 742-regulates the bolt preceding thread, and 743-regulates bolt indentation, and 742-regulates the bolt rear thread;
The 75-spring;
76-relief valve valve body, 761-valve opening, 762-draining hole, 763-equalizing orifice, 764-valve body outside thread, 765-valve body internal thread;
The 77-spool, 771-spool awl point, 772-spool ante-chamber, 773-spool back cavity, 774-draining hole.
Embodiment
In Fig. 2; disclosed a kind of large speed ratio oil hydraulic cylinder that adopts self-protection structure; mainly comprise: oil hydraulic pump 1, selector valve 2, bidirectional hydraulic lock 3, double-act-ing hydraulic J-Horner 4, fuel tank 5, piston rod 6, relief valve 7; wherein; double-act-ing hydraulic J-Horner 4 has A chamber 41 and B chamber 42, is provided with relief valve 7 between A chamber 41 and B chamber 42.
In Fig. 3, the head of piston rod 6 offers a descending step type inner chamber, and relief valve 7 is fixed on by being threaded in this step type inner chamber, and the opening end 66 of step type inner chamber is communicated with A chamber 41, and the top 65 of step type inner chamber is communicated with B chamber 42.This piston rod 6 comprises: the piston body of rod 60, piston bushing 61, piston sleeve 63, a plurality of seal ring 62,64, piston bushing 61 is fixed on the end of the piston body of rod 60 by fastening screw trip bolt 64, seal ring 62 fixed covers are on piston bushing 61, form sealing configuration between seal ring 62 and the hydraulic jack inboard wall of cylinder block 43, also be provided with a seal ring 64 between the piston body of rod 60 and the piston bushing.Piston sleeve 63 is enclosed within on the piston body of rod 60, the piston body of rod 60 heads are gradually wide stepped of external diameter, piston bushing 61 and piston sleeve 63 inboards are equipped with and the corresponding step in the piston body of rod 60 heads outside, piston bushing 61 is axially fixed in piston sleeve 63 on the piston body of rod 60, has the oil guiding hole 631 that is communicated with B chamber 42 and valve opening 761 respectively on the piston sleeve 63.Relief valve 7 is connected in the step type on the cavity wall by the thread helix on it.
In Fig. 4, this plug-in type relief valve 7 comprises: locking nut 72, Sealing 73,78, regulate bolt 74, spring 75, valve body 76, spool 77, valve body 76 is the tubular cavity, have valve opening 761 in the middle of the tubular cavity bottom, tubular cavity bottom sidewall has draining hole 762 and equalizing orifice 763, spring 75, valve body 76 and spool 66 are arranged in this tubular cavity, adjusting bolt 74 is threaded with cavity inner wall and seals by a Sealing 73, the awl point 771 of spool 77 inserts in the valve opening 761, the two ends of spring 75 are separately positioned in the groove 743 and spool back cavity 773 (groove of spool) of regulating bolt, locking nut 72 is arranged in to be regulated on the end that bolt 74 stretches out valve body 76 and withstands valve body 76, the draining hole 762 and the equalizing orifice 763 that are communicated with A chamber 41 are communicated with spool ante-chamber 772 respectively, spool back cavity 773, valve opening 761 is communicated with B chamber 42, the awl point 771 of spool 77 can be in A chamber 41, what move to form valve body 76 under the pressure effect in the elastic force of spring 75 and B chamber 42 in valve opening 7611 opens/closes state, also is with another Sealing 78 on the outer side wall between tubular cavity bottom draining hole 762 and the valve opening 761.Certainly, this equalizing orifice 763 can be arranged on the front end side wall of valve body 76, also can be arranged on the spool 77.
The valve opening 761 of relief valve 7 (P mouth) communicates with the B chamber 42 of double-act-ing hydraulic J-Horner 4, and its pressure affacts the front portion of spool 77, and the draining hole 762 of relief valve 7 (T mouth) communicate with the A chamber 41 of double-act-ing hydraulic J-Horner, and its pressure affacts spool 77 rear portions.Relief valve 7 is closed condition when static, and the valve opening 761 of relief valve 7 is not connected with draining hole 762.When double-act-ing hydraulic J-Horner 4 bearing thrust loads, draining hole 762 pressure raise, no matter but how high draining hole 762 pressure are, because relief valve 7 spools 17 rear portions are stressed stressed greater than the front portion, spool 77 can not move, and valve opening 761 can not opened, and A chamber 41 keeps working voltages and is unlikely thrust and diminishes.When piston rod 6 zero loads of double-act-ing hydraulic J-Horner 4 are stretched out, or greatly thrust load unloads suddenly, the increased pressure of valve opening 761 and when surpassing predetermined pressure, spool 77 is opened, pressure oil is by draining hole 762 earial drainages on the valve body 76, and like this, the high pressure in B chamber 42 will be let out to A chamber 41; After the pressure of valve opening 761 drops to predetermined pressure, spool 77 is closed under the effect of spring 75 again, the pressure that so not only can guarantee the B chamber 42 of double-act-ing hydraulic J-Horner 4 can not rise so high, and B chamber 42 still is airtight volume after guaranteeing pressure release, thereby guarantee that piston rod 6 is in axial accurate location.When 42 oil-feeds of the B chamber of double-act-ing hydraulic J-Horner 4, during piston rod 6 retraction, because the cracking pressure of relief valve 7 is greater than system works pressure, thereby the valve opening 761 of relief valve 7 can not opened, guarantee that piston rod 6 can bounce back smoothly, the working state of oil hydraulic cylinder can keep effectively normal all the time like this.
Installed the oil hydraulic cylinder of plug-in type relief valve 7 additional, protective function carries out automatically, only needs before assembling the oil pressure relief of relief valve 7 to be set, and need not to carry out otherwise adjustment, just can guarantee the reliable operation of this self-protection oil hydraulic cylinder.
In the present embodiment, the overflow set pressure of this relief valve 7 is to determine as follows.
The pressure p in B chamber during the beginning overflow
BPressure when being lower than oil hydraulic cylinder cylinder barrel generation plastic deformation, and certain margin of safety will be arranged.
If the oil hydraulic cylinder internal diameter of cylinder is D
1, the wall thickness of cylinder barrel thinnest part is δ, Tensile strength is σ
b, safety coefficient is n, if approximate by the calculating of thin-walled cylinder formula, the B cavity pressure p when then relief valve has just begun overflow
BShould be:
p
B＝2δσ
b/D
1/n (6)
For example, the oil hydraulic cylinder D of truck crane vertical hydraulic oil cylinder
1=125mm, δ=12.5mm, σ
b=600MPa, n=3, then
P
B＝2×12.5×600/125/3＝40(MPa)
Because relief valve 7 is fully immersed in the fluid, the back of spool 77 is always acting on the A cavity pressure, and the set pressure of general relief valve is meant the cracking pressure when drain tap (T mouth) pressure is zero, what cracking pressure overcame is spring force, so relief valve overflow set pressure need be converted and could determine.
If relief valve overflow set pressure is p, spring force is F, and the anterior orifice diameter of valve body 16 is D
2, then have:
F＝pπD
2 2/4 (7)
Have when being about to overflow:
P
B＝ip
A (8)
The stress balance side of spool 17 becomes
p
BπD
2 2/4＝p
AπD
2 2/4+F (9)
Bring formula (7), (8) into formula (9),
p＝(1-1/i)p
B (10)
The as above oil hydraulic cylinder in the example, i=2.78, then p=(1-1/2.78) * 40=25.6 (MPa)
The actual overflow set pressure of relief valve can be selected between 24 ~ 26MPa, and the set pressure area requirement is not harsh.
Such relief valve is installed in the oil hydraulic cylinder of last example, stretch out in the hydraulic cylinder piston rod zero load, or when greatly thrust load unloads suddenly, when the B cavity pressure reaches 40MPa, relief valve is just opened pressure release automatically, again because the hydraulic oil volumetric modulus of elasticity is higher, has only very little decrement, so, only need release the hydraulic oil of minute quantity, the B cavity pressure will descend rapidly, so the B cavity pressure can not reach the degree that causes cylinder barrel generation plastic deformation forever, B releases in the chamber hydraulic oil of minute quantity simultaneously, can not produce obviously influence to the extrusion of piston rod.
By a relief valve being installed in large speed ratio oil hydraulic cylinder inside; can form a oil hydraulic cylinder with self-protecting function; this has much better than anti-inefficacy ability than common large speed ratio oil hydraulic cylinder; and cost only improves about 1%; be a less investment, effective structural design, be worth on the large speed ratio oil hydraulic cylinder, applying.
Characteristics of the present invention are that relief valve is installed on oil hydraulic cylinder inside, because the oil hydraulic cylinder speed ratio is big, generally do not have enough spatial arrangement relief valves on the piston, and relief valve will be installed on the head of piston rod.The advantage of this structure
1. the processing of the processing of mounting hole key dimension and piston rod head is in same station, is convenient to shape in a clamping, simultaneously no strict coaxality requirement between mounting hole and each size of piston rod cylindrical.
2. have only the installation screw thread of relief valve and the coaxality between the seal ring hole to have relatively high expectations, but processing easily.
3. relief valve overflow set pressure wider range, the reliability height.
4. be not subjected to the outside dimensions spatial constraints, compact structure, on similar oil hydraulic cylinder, apply easily.
5. protective action automatically performs, and need not foreign intervention.
Above said content only is the present invention's preferred embodiment wherein, is not to be used for limiting practical range of the present invention; Be all equivalent variations and modifications of carrying out according to the present invention's design, the protection domain that is all claim of the present invention is contained.
Claims (14)
1, a kind of self-protection large speed ratio oil hydraulic cylinder, comprise: oil hydraulic pump and hydraulic oil container, selector valve, bidirectional hydraulic lock, have the double-act-ing hydraulic J-Horner in A chamber and B chamber, described oil hydraulic pump is connected to the A chamber of described double-act-ing hydraulic J-Horner successively by selector valve and bidirectional hydraulic lock, the B chamber of described double-act-ing hydraulic J-Horner is connected to hydraulic oil container by bidirectional hydraulic lock, selector valve successively; It is characterized in that,, also be provided with a relief valve between described A chamber and the B chamber in the inside of described double-act-ing hydraulic J-Horner.
2, self-protection large speed ratio oil hydraulic cylinder according to claim 1 is characterized in that described relief valve is fixedly installed on the head of described piston rod.
3, self-protection large speed ratio oil hydraulic cylinder according to claim 1 and 2; it is characterized in that; the head of described piston rod offers a descending step type inner chamber; adopt the relief valve of plug-in type structure to be fixed in the described step type inner chamber; the opening end of described step type inner chamber is communicated with described A chamber, and the top of described step type inner chamber is communicated with described B chamber.
4, self-protection large speed ratio oil hydraulic cylinder according to claim 3; it is characterized in that; described piston rod comprises the piston body of rod, piston bushing, a plurality of seal ring again; described piston bushing is fixed on the end of the described piston body of rod; described seal ring fixed cover on the described piston bushing and and described hydraulic jack inboard wall of cylinder block between form sealing configuration, be provided with sealing configuration between the described piston body of rod and the described piston bushing.
5; according to claim 3 or 4 described self-protection large speed ratio oil hydraulic cylinders; it is characterized in that; described plug-in type relief valve comprises again: locking nut; Sealing; regulate bolt; spring; valve body; spool; described valve body is the tubular cavity; have valve opening in the middle of the tubular cavity bottom; tubular cavity bottom sidewall has draining hole and equalizing orifice; described spring; valve body and spool are arranged in the described tubular cavity; described adjusting bolt and described cavity inner wall are threaded and seal by a Sealing; the awl point of described spool inserts in the described valve opening; the two ends of described spring are separately positioned in the groove of described adjusting bolt and spool; described locking nut is arranged in described adjusting bolt and stretches out on the end of described valve body and withstand described valve body; the chamber, front and back that draining hole that is communicated with described A chamber and equalizing orifice are communicated with described spool respectively; described valve opening is communicated with described B chamber; the awl point of described spool can be in described A chamber; in described valve opening, move the formation valve body under the pressure effect in spring force and B chamber and open/close state, on the outer side wall between described tubular cavity bottom draining hole and the valve opening, also be with another Sealing.
6, self-protection large speed ratio oil hydraulic cylinder according to claim 5; it is characterized in that; described piston rod also comprises another set of piston sleeve on described piston rod; described piston rod head is gradually wide stepped of external diameter; described piston bushing and piston sleeve inboard are equipped with and the corresponding step in the described piston rod head outside; described piston bushing is axially fixed in described piston sleeve on the described piston rod, has the oil guiding hole that is communicated with described B chamber and valve opening respectively on the described piston sleeve.
7, self-protection large speed ratio oil hydraulic cylinder according to claim 5; it is characterized in that; described plug-in type relief valve also comprises a valve bonnet; described valve bonnet is provided with a containing space; the end that described locking nut and adjusting bolt stretch out described valve body is contained in the described containing space; the opening of described valve bonnet is extended with bending edge, and described bending edge is stuck in the groove between described locking nut and the described valve body.
8, large speed ratio oil hydraulic cylinder according to claim 5 is characterized in that, the termination portion that described adjusting bolt stretches out described valve body one end also has to regulate revolves the hole.
9, self-protection large speed ratio oil hydraulic cylinder according to claim 3 is characterized in that, described relief valve spiral is connected on the interior cavity wall of described step type.
10, self-protection large speed ratio oil hydraulic cylinder according to claim 5 is characterized in that, also offers the screw thread that is connected with cavity wall in the described step type on the described valve body front end side wall.
11, self-protection large speed ratio oil hydraulic cylinder according to claim 5 is characterized in that, described equalizing orifice is arranged on the front end side wall of valve body, perhaps is arranged on the described spool.
12, a kind of manufacture method of self-protection large speed ratio hydraulic jack comprises the steps:
One oil hydraulic pump and hydraulic oil container are set, are used to provide and reclaim high-pressure and hydraulic oil;
One selector valve is set, is used for switching as required the oil circuit direction;
One two-way hydraulic lock is set, is used for the locking oil circuit, prevent that the oil cylinder piston bar from freely stretching;
One double-act-ing hydraulic J-Horner that has A chamber and a B chamber is set, is used for moving by promoting oil cylinder at A chamber and B chamber I/O hydraulic oil;
It is characterized in that in the inside of described double-act-ing hydraulic J-Horner, between described A chamber and the B chamber relief valve is set, when the B cavity pressure was higher than the A chamber and reach oil hydraulic cylinder security settings pressure, the high pressure oil in described B chamber leaked into described A chamber through described relief valve; Described security settings pressure is that hydraulic jack does not take place to be out of shape the safety pressure that lost efficacy because of cylinder barrel.
13, the manufacture method of self-protection large speed ratio hydraulic system according to claim 12 is characterized in that, the oil pressure relief of described relief valve is adjustable.
14, self-protection large speed ratio oil hydraulic cylinder according to claim 12 is characterized in that, the overflow set pressure of described relief valve can be undertaken by following formula:
p＝(1-1/i)p
B
Wherein, p
BB cavity pressure when just having begun overflow for relief valve, p
B=2 δ σ
b/ D
1/ n;
The oil hydraulic cylinder internal diameter of cylinder is D
1, the wall thickness of cylinder barrel thinnest part is δ, Tensile strength is σ
b, safety coefficient is n, i is a speed ratio.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100092762A CN1321270C (en) | 2004-06-29 | 2004-06-29 | Self-protection large gear ratio hydraulic cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100092762A CN1321270C (en) | 2004-06-29 | 2004-06-29 | Self-protection large gear ratio hydraulic cylinder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1594897A true CN1594897A (en) | 2005-03-16 |
| CN1321270C CN1321270C (en) | 2007-06-13 |
Family
ID=34662422
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100092762A Expired - Fee Related CN1321270C (en) | 2004-06-29 | 2004-06-29 | Self-protection large gear ratio hydraulic cylinder |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1321270C (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012083663A1 (en) * | 2010-12-20 | 2012-06-28 | 湖南三一智能控制设备有限公司 | Hydro-pneumatic suspension system and wheeled vehicle with the system |
| CN107485512A (en) * | 2017-08-29 | 2017-12-19 | 范师华 | A kind of intellectual nursing bed hydraulic regulation action bars |
| CN108005746A (en) * | 2017-12-29 | 2018-05-08 | 潍柴动力股份有限公司 | A kind of engine main oil gallery pressure limiting valve and engine |
| CN110454458A (en) * | 2019-09-12 | 2019-11-15 | 天津华征机械制造有限公司 | A kind of hydraulic re-railing block cylinder rod chamber decompression load releasing valve |
| CN112912632A (en) * | 2018-10-19 | 2021-06-04 | 株式会社普利司通 | Actuator |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101387308B (en) * | 2007-09-14 | 2012-11-28 | 陕西汽车集团有限责任公司 | Hydraulic support shaft control valve assembly |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001234901A (en) * | 2000-02-24 | 2001-08-31 | Komatsu Ltd | Hydraulic circuit for cylinder |
| CN2465011Y (en) * | 2001-01-20 | 2001-12-12 | 尹建 | Overflow valve for engineering machinery |
| JP4641674B2 (en) * | 2001-07-10 | 2011-03-02 | カヤバ工業株式会社 | Hydraulic cylinder |
| JP2003056515A (en) * | 2001-08-21 | 2003-02-26 | Shin Caterpillar Mitsubishi Ltd | Hydraulic cylinder with cushion mechanism |
-
2004
- 2004-06-29 CN CNB2004100092762A patent/CN1321270C/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012083663A1 (en) * | 2010-12-20 | 2012-06-28 | 湖南三一智能控制设备有限公司 | Hydro-pneumatic suspension system and wheeled vehicle with the system |
| CN107485512A (en) * | 2017-08-29 | 2017-12-19 | 范师华 | A kind of intellectual nursing bed hydraulic regulation action bars |
| CN108005746A (en) * | 2017-12-29 | 2018-05-08 | 潍柴动力股份有限公司 | A kind of engine main oil gallery pressure limiting valve and engine |
| CN108005746B (en) * | 2017-12-29 | 2024-04-16 | 潍柴动力股份有限公司 | Engine main oil duct pressure limiting valve and engine |
| CN112912632A (en) * | 2018-10-19 | 2021-06-04 | 株式会社普利司通 | Actuator |
| US11821114B2 (en) | 2018-10-19 | 2023-11-21 | Bridgestone Corporation | Actuator |
| CN110454458A (en) * | 2019-09-12 | 2019-11-15 | 天津华征机械制造有限公司 | A kind of hydraulic re-railing block cylinder rod chamber decompression load releasing valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1321270C (en) | 2007-06-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1046337C (en) | Pilot stage for pressure control valves | |
| DE102007016594B4 (en) | Rear wheel suspension device for two-wheeled vehicle | |
| CN2851679Y (en) | Hydraulic cylinder with mechanical lock | |
| EP1777177A1 (en) | Stop and damper module | |
| CN2709691Y (en) | Autoprotection large speed ratio hydraulic cylinder | |
| WO2014009115A1 (en) | Energy-recuperating fluid vibration damper | |
| DE3150643A1 (en) | HYDRAULIC TELESCOPE STAMP, ESPECIALLY FOR UNDERGROUND SCREAM EXTENSION, LIKE, IN PARTICULAR, SHIELD EXTENSION RACK | |
| CN1594897A (en) | Self-protection large gear ratio hydraulic cylinder | |
| CN2845947Y (en) | Digital control hydraulic double power stretcher | |
| WO2009132438A1 (en) | Multi-speed hydraulic jack | |
| DE19731139C2 (en) | Piston-cylinder unit, which is installed between a body and a wheel guide part of a vehicle | |
| CN107717429A (en) | Multistage super-pressure thin-walled hydraulic elongator for hub of wind power generator kingbolt | |
| CN205089722U (en) | Electricity liquid push rod convenient to adjust pressure | |
| CN109026889A (en) | Buffer overflow valve | |
| CN107120335B (en) | Hydraulic cylinder | |
| CN201407224Y (en) | Overflow valve | |
| CN103867524A (en) | Double-acting second-level hydraulic cylinder | |
| CN108825588A (en) | A kind of oil cylinder with protective device | |
| CN109058208A (en) | A kind of buffer overflow valve | |
| CN214661236U (en) | Multi-stage plunger oil cylinder | |
| CN210660816U (en) | Buffering self-adaptive adjusting device and hydraulic cylinder with same | |
| CN109162977B (en) | Rotary cushion valve | |
| CN208546381U (en) | A kind of plunger-type cylinder throttle buffering structure | |
| CN102704445A (en) | Self-locking device of hydraulic hoist | |
| CN207431702U (en) | For the multistage super-pressure thin-walled hydraulic elongator of hub of wind power generator kingbolt |
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 | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20090220 Address after: Futian 1, Zhongshan Avenue, Xuanhua hi tech Development Zone, Hebei, Zhangjiakou Patentee after: FOTON LOVOL INT HEAVY IND Co. Address before: Sha Yang Road, Shahe Town, Beijing, Changping District Patentee before: BEIQI FOTON MOTOR Co.,Ltd. |
|
| ASS | Succession or assignment of patent right |
Owner name: FUTIAN REBOLLEDO HEAVY MACHINERY CO., LTD. Free format text: FORMER OWNER: BEIQI FUTIAN CAR CO., LTD. Effective date: 20090220 |
|
| ASS | Succession or assignment of patent right |
Owner name: BEIQI FUTIAN AUTOMOBILE CO., LTD. Free format text: FORMER OWNER: FUKUDA HEAVY MACHINERY CO., LTD Effective date: 20100726 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| C56 | Change in the name or address of the patentee |
Owner name: FUKUDA HEAVY MACHINERY CO., LTD Free format text: FORMER NAME: FOTON LOVOL INTERNATIONAL HEAVY INDUSTRIES CO., LTD. |
|
| COR | Change of bibliographic data |
Free format text: CORRECT: ADDRESS; FROM: 075100 (FUKUDA COMPANY)NO.1,ZHONGSHAN STREET,XUANHUA NEW+HIGH DEVELOPMENT ZONE,ZHANGJIAKOU CITY,HEBEI PROVINCE TO: 102206 SHAYANG ROAD, SHAHE TOWN, CHANGPING DISTRICT, BEIJING |
|
| CP01 | Change in the name or title of a patent holder |
Address after: 075100, No. 1 Zhongshan street, Xuanhua hi tech Development Zone, Zhangjiakou, Hebei province (Futian company) Patentee after: FOTON HEAVY MACHINERY Co.,Ltd. Address before: 075100, No. 1 Zhongshan street, Xuanhua hi tech Development Zone, Zhangjiakou, Hebei province (Futian company) Patentee before: FOTON LOVOL INT HEAVY IND Co. |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20100726 Address after: 102206 Changping District City, Shahe, Sha Yang Road, Beijing Patentee after: BEIQI FOTON MOTOR Co.,Ltd. Address before: 075100, No. 1 Zhongshan street, Xuanhua hi tech Development Zone, Zhangjiakou, Hebei province (Futian company) Patentee before: FOTON HEAVY MACHINERY Co.,Ltd. |
|
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070613 Termination date: 20180629 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |