CN102155457A - Hydraulic oil cylinder, hydraulic buffering system, excavator and concrete pump truck - Google Patents
Hydraulic oil cylinder, hydraulic buffering system, excavator and concrete pump truck Download PDFInfo
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- CN102155457A CN102155457A CN 201110102731 CN201110102731A CN102155457A CN 102155457 A CN102155457 A CN 102155457A CN 201110102731 CN201110102731 CN 201110102731 CN 201110102731 A CN201110102731 A CN 201110102731A CN 102155457 A CN102155457 A CN 102155457A
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Abstract
The invention discloses a hydraulic oil cylinder which comprises a rod cavity end closure, a cylinder barrel, a piston rod, a piston and a rodless cavity end closure, wherein the inner chamber of the hydraulic cylinder barrel is divided into a rod cavity and a rodless cavity by the piston rod and the piston; the piston rod is provided with a buffering sleeve which comprises a first buffering sleeve and/or a second buffering sleeve; the buffering sleeve can slide along the axial direction of the piston rod; an axial throttling oil passage is arranged between the buffering sleeve and the piston rod; the first buffering sleeve is provided with a sealing end surface; a sealing end surface is arranged on the rod cavity end closure; hydraulic oil in the rod cavity is discharged to an oil passage through the throttling oil passage; the end surface of the second buffering sleeve is in contact with the sealing end surface of the rodless cavity end closure to form a sealing; and the hydraulic oil in the rodless cavity is discharged to the oil passage through the throttling oil passage. The invention provides a buffering mechanism of the hydraulic oil cylinder; and the buffering mechanism has longer service life, has lower requirement on the accuracy of manufacturing and is convenient for organizing production.
Description
The application be submitted that Patent Office of the People's Republic of China, application number are 201010235138.1 on 07 23rd, 2010 to, (this application technological scheme of asking for protection has been submitted utility application to denomination of invention on the same day for the Chinese patent application of " a kind of hydraulic jack and relevant apparatus thereof, and hydraulic buffer system, excavator and concrete mixer "; and fulfiled relevant formality) divide an application, its full content is by reference in conjunction with in this application.
Technical field
The present invention relates to the hydraulics field, especially relate to a kind of hydraulic jack.The present invention is provided for hydraulic buffer system, excavator and the concrete mixer of above-mentioned hydraulic jack simultaneously.
Background technique
Hydraulic jack is widely used parts in the engineering machinery, and in its working procedure, piston needs continuous to-and-fro motion.When piston rod reached limit position, piston end surface can produce very big impact to end cap, might cause the damage of hydraulic jack.For this reason, need damping device be set, avoid of the damage of above-mentioned that percussion hydraulic jack at this position.
Existing damping device is different according to hydraulic jack application and size, has very big difference.Small-sized oil cylinder can directly adopt stage clip as damping device, still, for the hydraulic jack of big cylinder diameter, big stroke, if adopt stage clip as damping device, obtain the enough springs of elasticity with being difficult to, and spring will soon damage owing to compressing repeatedly.Therefore, the hydraulic jack for big cylinder diameter, big stroke generally adopts hydraulic cushion mechanism shown in Figure 1.
Please referring to Fig. 1, this illustrates, and described damping device is included in big buffering ring of installing on the middle annular groove that the buffer position of piston rod offers 06 and the big cushion collar 04 that is enclosed within buffer position; Corresponding big cushion collar 04 in the lid oral area position of the rod chamber end cap 01 of oil cylinder, is provided with the buffering endoporus 07 that the external diameter of internal diameter and described big cushion collar 04 matches.When described piston rod stretched out, described big cushion collar 04 at first inserted in the described buffering endoporus 07, made the oil return circuit of rod chamber in the cylinder barrel 02 blocked, and meanwhile, the gap between big cushion collar 04 and the buffering endoporus 07 forms the throttling oil duct; Like this, piston 05 can continue to be subjected to throttling oil duct damping function simultaneously to stretching out the direction motion, and its movement velocity descends.And it is near more that piston 05 stretches out the final position from piston rod 03, and the throttling oil duct between big cushion collar 04 and the buffering endoporus 07 is long more, and the damping of throttling oil duct is big more, and the motion of piston 05 is slow more, stretches out the final position up to finally arriving piston rod 03 stably.
Above-mentioned damping mechanism is widely used in the hydraulic jack of big cylinder diameter, big stroke at present, for hydraulic jack provides buffering guarantor preferably.
But also there is obvious defects in above-mentioned damping mechanism.At first, in above-mentioned big cylinder diameter, big stroke hydraulic oil cylinder, hydraulic jack often is operated under big load, the high-frequency operating conditions.For example, the driving oil cylinder of the occasions such as digging arm driving of excavator use.At this moment, the big cushion collar 04 in the above-mentioned damping mechanism need insert described buffering endoporus 07 repeatedly with high speed, and matching gap between the two was original just very little, and piston rod 03 is very heavy, and it is easily to lopsidedness under the effect of gravity; Therefore, the hydraulic jack that above-mentioned occasion is used is easy to occur cushion collar 04 can't insert the damping mechanism fault that cushions in the endoporus 07, causes whole hydraulic jack normally not use.
Another key issue of above-mentioned damping mechanism is that the outside dimension of big cushion collar 04 must accurately cooperate with the internal diameter of described buffering endoporus 07, otherwise just can't realize buffer function; It is high that this just causes the accuracy of manufacturing of this damping mechanism to require, and the manufacture level of general producer is difficult to meet the requirements.Because the excessive demand of above-mentioned accuracy of manufacturing causes the hydraulic jack of big stroke, big cylinder diameter to become the bottleneck problem that an engineering machinery such as excavator is produced, and has seriously limited the throughput of each manufacturer that is in the downstream link.
Summary of the invention
The invention provides a kind of hydraulic jack, the damping mechanism of this hydraulic jack can realize having longer working life by cushioning effect reliably under big load, high-frequency operating mode.And the accuracy of manufacturing of this hydraulic jack requires low, is convenient to tissue production.This hydraulic jack is specially adapted to the manufacturing of big cylinder diameter, long stroke hydraulic oil cylinder, easy processing, steadily good buffer effect.
Hydraulic buffer system, excavator and concrete mixer that the present invention provides above-mentioned hydraulic jack to use simultaneously.
Hydraulic jack provided by the invention, comprise rod chamber end cap (1), cylinder barrel (2), piston rod (3), piston (6) and rodless cavity end cap (12), described rod chamber end cap (1) is provided with oil duct (B), and described rodless cavity end cap (12) is provided with oil duct (A), it is characterized in that:
Also be provided with at least one throttling oil groove (301a, 301b), described piston rod (3) is provided with at least one cushion collar, described cushion collar comprises first cushion collar (4) that is positioned at rod chamber and/or second cushion collar (11) that is positioned at rodless cavity, and described cushion collar (4,11) can endwisely slip along described piston rod (3);
Described first cushion collar (4) is provided with seal face (401), rod chamber end cap (1) is provided with seal face (101), stretch out in the movement process at piston, the first cushion collar end face (401) can contact with the seal face (101) of described rod chamber end cap (1) and form sealing surface, and sealing surface can be expelled to oil duct (B) by throttling oil duct (301a) by the hydraulic oil of piston one side;
Described second cushion collar (11) is provided with seal face (111), described rodless cavity end cap (12) is provided with seal face (121), in the piston-retraction movement process, the described second cushion collar end face (121) can contact with the seal face (121) of described rodless cavity end cap (12) and form sealing, and sealing surface can be expelled to oil duct (A) by throttling oil duct (301b) by the hydraulic oil of piston one side.
Preferably, (301a, 301b) straight line is arranged between described piston rod (3) and the described cushion collar (4,11) described throttling oil duct vertically.
Preferably, when described piston rod (3) when extending out to stroke terminal, described first cushion collar (4) is from its terminal point (L1) at regular intervals that slides towards described piston (6) direction.
Preferably, when described piston rod (3) when being retracted to stroke terminal, described second cushion collar (11) is from its terminal point (L2) at regular intervals that slides towards described piston (6) direction.
Preferably, when the seal face (401) of described first cushion collar (4) contacts with the seal face (101) of described rod chamber end cap (1) when forming sealing surface, the pressure oil in the rod chamber to the axial action area of described first cushion collar (4) greater than the axial action area of the hydraulic oil in the described oil channel (B) to described first cushion collar (4).
Preferably, when the seal face (111) of described second cushion collar (11) contacts with the seal face (121) of described rodless cavity end cap (12) when forming sealing, the pressure oil in the rodless cavity to the axial action area of described second cushion collar (11) greater than the axial action area of the pressure oil in the described oil channel (A) to described second cushion collar (11).
Preferably, the seal face (401) of described first cushion collar (4) contacts with the seal face (101) of described rod chamber end cap (1) and forms face seal or linear sealing.
Preferably, the seal face (111) of described second cushion collar (11) contacts with the seal face (121) of described rodless cavity end cap (12) and forms face seal or linear sealing.
Preferably, go up to the slip of described piston (6) direction at described piston rod (3) when described cushion collar (4,11), (301a, 301b) cross-section area is along with diminishing for described throttling oil duct.
Preferably, be provided with in described cylinder barrel (2) cavity and be used for the elastic element (5,7) that described cushion collar (4,11) resets.
Preferably, described piston rod (3) is provided with many circumferential balance oil grooves (302a, 302b) with the matching surface of described cushion collar (4,11).
Preferably, described throttling oil duct (301a, 301b) is that axial straight line is arranged on the throttling oil groove on described piston rod (3) outer surface, and its cross-section area diminishes gradually towards described piston (6) direction.
Preferably, described throttling oil duct (301a, 301b) is arranged on the throttling inclined-plane of described cushion collar (4,11) and described piston rod (3) sliding area for axial straight line.
Preferably, described throttling oil duct (301a, 301b) is included in the axially extended oil duct of offering in the described piston rod (3) (3013), and offer at described piston rod (3) outer surface several be communicated with the throttle orifice (3014) of described oil duct (3013), several described throttle orifices (3014) are axial arranged along described piston rod (3) surface.
Preferably, the aperture of described throttle orifice (3014) diminishes gradually to described piston (6) direction.
Preferably, described throttling oil duct (301a, 301b) comprises the first section throttling oil duct (3012) that is positioned at its entrance point and is positioned at second section throttling road (3011) of its outlet end, described first section throttling oil duct (3012) is for being arranged on the throttling oil groove on described piston rod (3) surface, and described second section throttling oil duct (3012) is for being arranged on the inner oil duct of described piston rod (3) or described cushion collar (4,11).
Preferably, described first section throttling oil duct (3012) cross-section area diminishes gradually to described piston direction.
Preferably, described piston rod (3) comprises piston rod body and spacer shell (304), described spacer shell (304) is sleeved on the described piston rod body, described cushion collar (4,11) is enclosed within on the described spacer shell (304), and described throttling oil duct (301a, 301b) is arranged on the described spacer shell (304).
Preferably, described piston rod (3) comprises piston rod body (3a) and buffer shaft (3b), described piston rod body (3a) and described buffer shaft (3b) interconnect, described second cushion collar (11) is arranged on the described buffer shaft (3b), and described throttling oil duct (301b) is arranged on the described buffer shaft (3b).
A kind of hydraulic jack provided by the invention, its beneficial effect is:
One, cushion collar are provided with seal face, rodless cavity end cap and/or rod chamber end cap are provided with seal face, both contact and form sealing, and the hydraulic oil of rodless cavity and/or rod chamber makes its throttling oil duct that passes through to be provided with on cushion collar and piston rod discharge oil channel.Thereby make the hydraulic oil that is closed, produce suitable compensator or trimmer pressure and act on the piston oil extraction side, resist mutually with the inertial force of piston, to reach the purpose of retarding braking; This mechanism's throttling buffering is very steadily reliable, has avoided damping mechanism to produce mechanical failure.In preferred embodiments, the circulation area of throttling oil duct changes, and has played the purpose of variable throttling buffering.Cushion collar and piston rod and throttling oil duct interact and have played the effect of variable throttling valve.
When two, piston rod was retracted to stroke terminal, the second cushion collar no show final position still can be towards the piston direction determining deviation that slides.When piston rod stretches out, oil channel A oil-feed, promoting second cushion collar under the effect of hydraulic oil slides to piston direction, compression reseting spring, the seal face of second cushion collar separates with the seal face of rodless cavity end cap, oil channel A directly communicates with rodless cavity, and hydraulic oil enters in the rodless cavity, promotes piston to left movement.Second cushion collar and rodless cavity end cap interact and have played the effect of one-way valve.Can make the rodless cavity quick oil feeding, promote piston motion.If second cushion collar does not possess the effect of one-way valve, can not make hydraulic oil enter rodless cavity fast, in the time of will causing piston rod to stretch out, start slowly, even piston rod can't stretch out motion.
When piston rod extend out to stroke terminal, the first cushion collar no show final position still can be towards the piston direction determining deviation that slides.When piston rod is regained, oil channel B oil-feed, promoting first cushion collar under the effect of hydraulic oil slides to piston direction, compression reseting spring, the seal face of first cushion collar separates with the seal face of rod chamber end cap, oil channel B directly communicates with rod chamber, and hydraulic oil enters in the rod chamber, promotes piston motion.First cushion collar and rod chamber end cap interact and have played the effect of one-way valve.Can make the rod chamber quick oil feeding, promote piston motion.If first cushion collar does not possess the effect of one-way valve, can not make its hydraulic oil enter rod chamber fast, in the time of will causing piston rod to regain, start slowly, even piston rod can't recovery movement.
Three, in the hydraulic jack of big cylinder diameter and long stroke, form reliable sealing surface between cushion collar and the rodless cavity end cap in order to make, rely on spring force foundation to seal very difficult the realization, neither be optimum.Hydraulic jack provided by the invention, when piston rod was retracted to setpoint distance before the stroke terminal, the rodless cavity end cap contact with second cushion collar, and the hydraulic oil in the rodless cavity is closed in the oil pocket of setting, the hydraulic fluid pressure rising in the rodless cavity.Because of pressure oil inequality to the second cushion collar axial action area, the pressure oil in the rodless cavity to the axial action area of second cushion collar greater than the axial action area of the hydraulic oil in the oil channel A to second cushion collar.The both sides of such second cushion collar just form pressure reduction.Second cushion collar makes to produce extruding formation sealing between second cushion collar and the rodless cavity end cap under the effect of pressure oil, forms reliable sealing surface with the rodless cavity end cap.Hydraulic oil in the rodless cavity is expelled to oil duct A by the throttling oil duct; Thereby solved the very difficult difficult problem that forms of sealing surface.
When piston rod 3 extend out to setpoint distance before the stroke terminal, the rod chamber end cap contact with first cushion collar, and the hydraulic oil in the rod chamber is closed in the oil pocket of setting, the hydraulic fluid pressure rising in the rod chamber.Because of pressure oil inequality to the first cushion collar axial action area, the pressure oil in the rod chamber to the axial action area of first cushion collar greater than the axial action area of the hydraulic oil in the oil channel B to first cushion collar.The both sides of such first cushion collar just form pressure reduction.First cushion collar makes to produce extruding formation sealing between first cushion collar and the rod chamber end cap under the effect of pressure oil, forms reliable sealing surface with the rod chamber end cap.Hydraulic oil in the rod chamber is expelled to oil duct by the throttling oil duct; Thereby solved the very difficult difficult problem that forms of sealing surface.
Four, between cushion collar and piston, Returnning spring is set, the one, during for the piston rod backhaul, start fast; The 2nd, for the buffering between cushion collar and rodless cavity and/or the rod chamber end cap with reset, also can be used for seal action.
Its five, many circumferential balance oil grooves of cushion collar and piston rod matching surface design are in order to improve cushion collar and piston rod working life.
Its six, the throttling oil duct is set to the straight line throttling oil duct of tapering or throttling inclined-plane, is steadily to slow down and instantaneous pressure not occur excessive, the mode of the variable throttling of employing for piston rod and piston.This kind structure easy processing, good buffer effect, long service life.
Its seven, for convenience at many of the piston rod machining high-precision circumferential balance oil grooves and throttling oil duct, adding at piston rod increases a spacer shell, many circumferential balance oil grooves and the processing of throttling oil duct are on spacer shell; Perhaps piston rod is divided into two sections and processes, be positioned at one section body of processing and connect piston rod separately of rodless cavity by Placements such as screw threads.
Description of drawings
Fig. 1 is a kind of hydraulic jack structural representation of prior art;
Fig. 2 is a kind of hydraulic jack provided by the invention, the structural representation of first kind of embodiment;
Fig. 3 is the piston rod design of part schematic representation among Fig. 2;
Fig. 4 is that the A-A of Fig. 3 is to view;
Fig. 5 is that the C-C of Fig. 3 is to view;
Fig. 6 is that the B-B of Fig. 3 is to view;
Fig. 7 is the cushion collar design of part schematic representation among Fig. 2;
Fig. 8 is that first cushion collar of a kind of hydraulic jack of providing of Fig. 2 is in the buffer status structural representation;
Fig. 9 is that first cushion collar of a kind of hydraulic jack of providing of Fig. 2 is in buffering done state structural representation;
Figure 10 is that second cushion collar of a kind of hydraulic jack of providing of Fig. 2 is in buffering shape structural representation;
Figure 11 is that second cushion collar of a kind of hydraulic jack of providing of Fig. 2 is in buffering done state structural representation;
Figure 12 is a kind of hydraulic jack provided by the invention, the structural representation of second kind of embodiment;
Figure 13 is a kind of hydraulic jack provided by the invention, the structural representation of the third embodiment;
Figure 14 is a kind of hydraulic jack provided by the invention, the structural representation of the 4th kind of embodiment;
Figure 15 is a kind of hydraulic jack provided by the invention, the structural representation of the 5th kind of embodiment;
Figure 16 is a kind of hydraulic jack provided by the invention, the structural representation of the 6th kind of embodiment;
Figure 17 is a kind of hydraulic jack provided by the invention, the structural representation of the 7th kind of embodiment;
Figure 18 is a kind of hydraulic jack provided by the invention, the structural representation of the 8th kind of embodiment;
Figure 19 is a kind of hydraulic jack provided by the invention, the structural representation of the 9th kind of embodiment;
Figure 20 is a kind of hydraulic jack provided by the invention, the structural representation of the tenth kind of embodiment;
Figure 21 is a kind of hydraulic jack provided by the invention, the structural representation of the 11 kind of embodiment.
Embodiment
In order to make those skilled in the art person understand technical solution of the present invention better, the present invention is described in further detail below in conjunction with the drawings and specific embodiments.
Please refer in first kind of embodiment of Fig. 2 to Figure 11, comprise rod chamber end cap 1, cylinder barrel 2, piston rod 3, piston 6 and rodless cavity end cap 12, rod chamber end cap 1 is provided with oil channel B, rodless cavity end cap 12 is provided with oil channel A, piston rod 3 and piston 6 are divided into rod chamber and rodless cavity with the inner chamber of hydraulic cylinder 2, oil channel B and oil channel A communicate with the oil circuit of hydraulic system, are the axial oil duct that is opened on the hydraulic jack.Oil channel B is included in the oil duct that the gap forms between the oil channel hole offered on the rod chamber end cap 1 and piston rod 3 and the rod chamber end cap 1, extends on the seal face 101 of rod chamber end cap 1.
Oil channel B is included in the oil duct that the gap forms between the oil channel hole offered on the rod chamber end cap 1 and piston rod 3 and the rod chamber end cap 1, extends on the seal face 101 of rod chamber end cap 1.Oil channel B also can directly be connected with oil channel A.
Oil channel A extends on the seal face 121 of rodless cavity end cap 12, offers the cavity of the buffer shaft 3b that holds piston rod 3 tail ends on it.Oil channel B also can directly be connected with oil channel A.
Setting is positioned at first cushion collar 4 of rod chamber and second cushion collar 11 of rodless cavity on the piston rod 3, and can endwisely slip along piston rod 3.Be provided with axial throttling oil duct 301a between first cushion collar 4 and the piston rod 3, be provided with axial throttling oil duct 301b between second cushion collar 11 and the piston rod 3; Throttling oil duct 301a and throttling oil duct 301b can have multiple choices, comprise that cross section is U-shaped, V-arrangement, type such as square.
The seal face 401 of first cushion collar 4 contacts with the seal face 101 of rod chamber end cap 1 and forms sealing can be face seal, also can be linear sealing.For example: in first kind of embodiment, seal face 401 forms plane sealing with seal face 101 for fitting; In the 6th kind of embodiment, as shown in figure 16, seal face 401 is provided with linear seal ring and the applying of seal face 101 planes forms linear sealing.In the 7th kind of embodiment, as shown in figure 17, seal face 101 is the conical surface, and seal face 401 contacts with seal face 101 and forms linear sealing.In the 8th kind of embodiment, as shown in figure 18, seal face 401 and seal face 101 are the conical surface, and the conical surface and the conical surface are fitted and formed face seal.Except that above-mentioned, also has alternate manner, as forms such as curved surface sealings.
In like manner, the seal face 111 of second cushion collar 11 contacts with the seal face 121 of rodless cavity end 12 and forms sealing can be face seal, also can be linear sealing.For example: in first kind of embodiment, seal face 111 forms plane sealing with seal face 121 for fitting; In the 9th kind of embodiment, as shown in figure 19, seal face 111 is provided with linear seal ring and the applying of seal face 121 planes forms linear sealing.In the tenth kind of embodiment, as shown in figure 20, seal face 111 and seal face 121 are the conical surface, and the conical surface and the conical surface are fitted and formed face seal.In the 11 kind of embodiment, as shown in figure 21, seal face 121 is the conical surface, and seal face 111 contacts with seal face 121 and forms linear sealing.
When piston rod 3 extend out to setpoint distance before the stroke terminal, rod chamber end cap 1 contact with first cushion collar 4, and the hydraulic oil in the rod chamber is closed in the oil pocket of setting, the hydraulic fluid pressure rising in the rod chamber.Because of pressure oil inequality to cushion collar axial action area, the pressure oil in the rod chamber to the axial action area of first cushion collar 4 greater than the axial action area of the pressure oil in the oil channel B to first cushion collar 4.The both sides of such first cushion collar 4 just form pressure reduction.First cushion collar 4 makes and produces extruding formation sealing between first cushion collar 4 and the rod chamber end cap 1 under the effect of pressure oil, forms reliable sealing surface with rod chamber end cap 1.Pressure oil in the rod chamber makes it be expelled to oil channel B by throttling oil duct 301a; Thereby solved the very difficult difficult problem that forms of sealing surface.
In like manner, when piston rod 3 was retracted to setpoint distance before the stroke terminal, rodless cavity end cap 12 contact with second cushion collar 11, and the hydraulic oil in the rodless cavity is closed in the oil pocket of setting, the hydraulic fluid pressure rising in the rodless cavity.Because of pressure oil inequality to the axial action area of second cushion collar 11, the pressure oil in the rodless cavity to the axial action area of second cushion collar 11 greater than the axial action area of the pressure oil in the oil channel A to second cushion collar 11.The both sides of such second cushion collar 11 just form pressure reduction.Second cushion collar 11 makes and produces extruding formation sealing between second cushion collar 11 and the rodless cavity end cap 12 under the effect of pressure oil, forms reliable sealing surface with rodless cavity end cap 12.Pressure oil in the rodless cavity makes it be expelled to oil channel A by throttling oil duct 301b; Thereby solved the very difficult difficult problem that forms of sealing surface.
The seal face 401 of first cushion collar 4 is all blocked oil channel B and is directly communicated with rod chamber after contacting with the seal face 101 of rod chamber end cap 1 and forming sealing.Also can partly block oil channel B directly communicates with rod chamber.Pressure oil in the rod chamber makes it be expelled to oil channel B by throttling oil duct 301a.Because of throttling oil duct 301a oil drain quantity is little, thereby make the hydraulic oil that is closed, produce suitable compensator or trimmer pressure and act on the piston 6 oil extraction sides, resist mutually with the inertial force of piston, to reach the purpose of retarding braking, the throttling buffering is very steadily reliable, has avoided damping mechanism to produce mechanical failure.
In like manner, the seal face 111 of second cushion collar 11 is all blocked oil channel A and is directly communicated with rod chamber after contacting with the seal face 121 of rodless cavity end cap 12 and forming sealing.Also can partly block oil channel A directly communicates with rodless cavity.Pressure oil in the rodless cavity makes it be expelled to oil channel A by throttling oil duct 301b.Because of throttling oil duct 301b oil drain quantity is little, thereby make the hydraulic oil that is closed, produce suitable compensator or trimmer pressure and act on the piston 6 oil extraction sides, resist mutually with the inertial force of piston, to reach the purpose of retarding braking, the throttling buffering is very steadily reliable, has avoided damping mechanism to produce mechanical failure.
The structural type of throttling oil duct 301a, 301b, can be according to throttling oil duct 301a, 301b cross-section area (being circulation area), can change automatically in the hydraulic jack buffering course and classify, circulation area become permanent throttling usually, and circulation area is changed into variable throttling.This has the multiple choices form, for example:
In first kind of mode of execution of the present invention, throttling oil duct 301a, 301b are arranged on the sliding area of piston rod 3 and first cushion collar 4 and second cushion collar 11, straight line throttling oil groove for the band tapering, the throttling oil groove degree of depth is successively decreased towards piston 6 directions, 4 throttling oil grooves of equal distribution are realized the steadily effect of buffering of variable throttling on the outer surface of piston rod 3.
In second kind of mode of execution of the present invention (shown in Figure 11), throttling oil duct 301a, 301b throttling inclined-plane on piston rod 3, offering, the throttling inclined-plane rises gradually towards piston direction, and promptly the throttling inclined-plane successively decreases towards the piston direction cross-section area, realizes the steadily effect of buffering of variable throttling.
In the 5th kind of mode of execution of the present invention (shown in Figure 14), on the sliding area of the piston rod 3 and first cushion collar 4, be provided with spacer shell 304.The throttling oil duct 301a that offers on the spacer shell 304 comprises first section throttling oil duct 3012 that is positioned at its entrance point and the second section throttling oil duct 3011 that is positioned at its outlet end, first section throttling oil passage 3012 is the straight line throttling oil groove that is arranged on the band tapering of spacer shell 304, and the throttling oil groove degree of depth is successively decreased towards piston 6 directions; Second section throttling oil duct 3011 realized the steadily effect of buffering of variable throttling for being arranged on the oil duct of spacer shell 304 inside.
In the 6th kind of mode of execution of the present invention (shown in Figure 15), on the sliding area of the piston rod 3 and first cushion collar 4, be provided with spacer shell 304.The throttling oil duct 301a that offers on the spacer shell 304 is included in the axially extended oil duct 3013 that spacer shell 304 inside are offered, and offer at spacer shell 304 outer surfaces several be communicated with the throttle orifice 3014 of oil ducts 3013, several throttle orifices 3014 are axial arranged along spacer shell 304.When first cushion collar 4 slided towards piston 6 directions, the quantity of the throttle orifice 3014 of first cushion collar, 4 sealings was progressively increased gradually, causes the circulation area of throttling oil duct 301a to successively decrease gradually, realized the steadily effect of buffering of variable throttling.Also can successively decrease gradually towards piston 6 directions in the aperture of throttle orifice 3014, reach the purpose of permanent retardation.
Exemplify the embodiment except that above-mentioned, throttling oil duct 301a, 301b can also be the permanent throttlings of employing, be arranged on the cushion collar 4,11.Throttling oil duct 301a, 301b successively decrease towards the piston direction cross-section area, can be that the degree of depth and/or width successively decrease.In the embodiments of the present invention, throttling oil duct 301a, 301b are arranged on the sliding area of piston rod 3 and cushion collar 4,11, are the straight line throttling oil groove of band tapering, and the throttling oil groove degree of depth is successively decreased towards piston 6 directions.To compare processing cost low with the helix throttling oil duct of different depth, and the helix throttling oil duct processing of different depth is very difficult, and processing cost is higher, and the machining accuracy of the spiral degree of depth is uncontrollable, can not reach desirable cushioning effect.The straight line throttling oil groove easy processing of band tapering, the machining accuracy of tapering is controlled easily, can reach desirable cushioning effect.First kind of mode of execution of the present invention is optimal case.
When piston rod 3 extend out to stroke terminal, first cushion collar, 4 no show final positions still can be towards the piston direction determining deviation L1 that slides.When piston rod 3 is regained, oil channel B oil-feed, promoting first cushion collar 4 under the effect of pressure oil slides to piston 6 directions, compress first Returnning spring 5, the seal face 401 of first cushion collar 4 separates with the seal face 101 of rod chamber end cap 1, oil channel B directly communicates with rod chamber, and hydraulic oil enters in the rod chamber, promotes piston 6 motions.Piston rod 3 is in the withdrawal process, and first cushion collar 4 interacts with rod chamber end cap 1 and played the effect of one-way valve.The spacing L1 of first cushion collar 4 between its terminal point that slides towards piston 6 directions.L1 is big more, and the seal face 401 of first cushion collar 4 is just big more with seal face 101 separating distances of rod chamber end cap 1, and the flow that hydraulic oil enters in the rod chamber is just many more.L1 is more little, and the seal face 401 of first cushion collar 4 is just more little with seal face 101 separating distances of rod chamber end cap 1, and the flow that hydraulic oil enters in the rod chamber is just more little.Spacing L1 must make its oil channel B directly communicate with rod chamber.
When piston rod 3 was retracted to stroke terminal, second cushion collar, 11 no show final positions still can be towards the piston direction determining deviation L2 that slides.When piston rod 3 stretches out, oil channel A oil-feed, promoting second cushion collar 11 under the effect of pressure oil slides to piston 6 directions, compress second Returnning spring 7, the seal face 111 of second cushion collar 11 separates with the seal face 121 of rodless cavity end cap 12, oil channel A directly communicates with rodless cavity, and hydraulic oil enters in the rodless cavity, promotes piston 6 motions.Piston rod 3 is in the process of stretching out, and second cushion collar 11 interacts with rodless cavity end cap 12 and played the effect of one-way valve.The spacing L2 of second cushion collar 11 between its terminal point that slides towards piston 6 directions.L2 is big more, and the seal face 111 of second cushion collar 11 is just big more with seal face 121 separating distances of rod chamber end cap 12, and the flow that hydraulic oil enters in the rodless cavity is just many more.L2 is more little, and the seal face 111 of second cushion collar 11 is just more little with seal face 121 separating distances of rod chamber end cap 12, and the flow that hydraulic oil enters in the rodless cavity is just more little.The size of spacing L2 must make its oil channel A directly communicate with rod chamber.
In order to realize cushion collar 4,11 in piston rod 3 smooth sliding, guarantee working life and performance, be provided with many circumferential balance oil groove 302a, 302b between cushion collar 4,11 and the piston rod 3; Balance oil groove 302a, 302b are provided with on piston rod 3 outer surfaces, also can be arranged on cushion collar 4,11 internal surfaces.Piston rod 3 cooperates outer surface to carry out the chromium plating processing with cushion collar 4,11, improve hardness and surface quality.
For making first cushion collar, 4 location reliable, piston rod 3 is provided with the shaft shoulder 303 that is used for first cushion collar, 4 location.For guaranteeing that the hydraulic jack buffering obviously reaches piston 6 backhauls and starts soon, be provided with first Returnning spring, 5, the first Returnning springs, 5 one ends between first cushion collar 4 and the piston 6 and be resisted against on the piston 6, the other end is resisted against on first cushion collar 4; First Returnning spring 5 is respectively applied for first cushion collar 4 is resetted and the buffering effect.When hydraulic jack is not in buffer status, first cushion collar 4 under the active force of first Returnning spring 5, first cushion collar 4 be resisted against the shaft shoulder 303.Offer oil-discharge trough D on the shaft shoulder 303, oil-discharge trough D communicates with throttling oil duct 301a.For first cushion collar 4 is located, structures such as back-up ring can be set on piston rod 3 also on piston rod 3.
For making second cushion collar, 11 location reliable, be provided with the shoulder that ends that is used for second cushion collar, 11 location at piston rod 3 tail ends.End shoulder and comprise card key 10, card keycap 8 and back-up ring 9, card key 10 is that two semi-annular shape structures are assemblied in piston rod 3 tail ends and only take on accordingly in the groove, and card keycap 8 is used for fixing card key 10 blocking between key 10 and the back-up ring 9; Back-up ring 9 is used for card keycap 8 location.Card key 10 cross sections are the L type, offer oil-discharge trough E on its outer surface, and card keycap 8 cross sections are square.Second cushion collar 11 and hydraulic oil are very big to the active force of card key 10, in order to prevent that active force from causing damage to card keycap 8 and back-up ring 9, the cross section of card key 10 is L shaped for being designed to, and the cross section of card keycap 8 is square for being designed to, active force is passed on the piston rod 3 by the card key 10 of L type.Thereby solved because of second cushion collar 11 and hydraulic oil are very big to the active force of card key 10, and card keycap 8 and back-up ring 9 have been caused the problem of damage.
Seal by O shape circle+Glais ring form Sealing (K08-D) between rod chamber end cap 1 and rodless cavity end cap 12 and the cylinder barrel 2.Rod chamber end cap 1 is provided with and stops shoulder 102, is used for piston 6 left ends spacing; Rodless cavity end cap 12 is provided with and stops shoulder, is used for piston 6 right-hand members spacing.
Hydraulic jack working procedure: when piston rod 3 stretches out, be piston 6 when left movement, piston rod 3 is in the withdrawal end-of-travel position, second cushion collar 11 is in the contact seal state with rodless cavity end cap 12, in order to make the rodless cavity quick oil feeding, promote piston rod 3 and stretch out motion.Second cushion collar 11 also has certain spacing L2 from the terminal point that it slides towards piston 6 directions, and second cushion collar 11 compresses second Returnning spring 7 under the effect of hydraulic oil, slide towards piston 6 directions.Thereby the seal face 111 of second cushion collar 11 separates with the seal face 121 of rodless cavity 12, and at this moment, second cushion collar 11 interacts with rodless cavity end cap 12 and plays the effect of one-way valve.
Pressure oil enters in the rodless cavity, promotes piston 6 to left movement.Rod chamber hydraulic oil is discharged through oil channel B, and in the certain distance before piston rod 3 extend out to stroke terminal, the end face 401 of cushion collar 4 contacts with rod chamber end face 101 and forms sealing, and blocking-up oil duct B is all or part of directly directly to communicate with rod chamber.Rod chamber pressure oil makes it be expelled to oil channel B by throttling oil duct 301a between first cushion collar 4 and the piston rod 3 and oil-discharge trough D.Because of throttling oil duct 301a oil drain quantity is little, act on the piston 6 oil extraction sides thereby make the hydraulic oil that is closed produce suitable compensator or trimmer pressure, resist mutually with the inertial force of piston.Hydraulic jack begins to enter left buffer status, along with piston rod 3 continues to stretch out, piston 6 continues to left movement, first cushion collar, 4 relative piston rods 3 slide to the right, and the circulation area of the throttling oil duct 301a between first cushion collar 4 and the piston rod 3 diminishes gradually, and the oil extraction flow diminishes, the compensator or trimmer pressure that rod chamber produces acts on the piston 6 oil extraction sides to be increased gradually, piston 6 speed reduce gradually, reach the purpose of retarding braking, realize steady buffer deceleration effect.Stop shoulder 102 the time when what piston 6 left sides were adjacent to rod chamber end cap 1, piston 6 is no longer to left movement, and piston rod 3 extend out to stroke terminal, and whole buffering course finishes.
When piston rod 3 is regained, when promptly piston 6 moves right.Piston rod 3 is in and stretches out end-of-travel position, and first cushion collar 4 is in the contact seal state with rod chamber end cap 1, in order to make the rod chamber quick oil feeding, promotes piston rod 3 recovery movements.First cushion collar 4 also has certain spacing L1 from the terminal point that it slides towards piston 6 directions, and first cushion collar 4 is under the effect of hydraulic oil, and pressure spring 5 slides towards piston 6 directions.Thereby the seal face 401 of first cushion collar 4 separates with the seal face 101 of rod chamber 1, this moment first cushion collar 4 in piston rod 3 withdrawal processes, interact with rod chamber end cap 1 and to play the effect of one-way valve.
Hydraulic oil enters rod chamber from oil duct B, promotes piston 6 and moves right, and piston rod 3 is regained.Rodless cavity hydraulic oil is discharged through oil duct A, and in the certain distance before piston rod 3 is retracted to stroke terminal, the end face 111 of second cushion collar 11 contacts with the end face 121 of rodless cavity end cap and forms sealing, and blocking-up oil duct A is all or part of directly to communicate with rodless cavity.Rodless cavity pressure oil makes it be expelled to oil channel A by throttling oil duct 301b between second cushion collar 11 and the piston rod 3 and oil-discharge trough E.Because of throttling oil duct 301b oil drain quantity is little, thereby make the hydraulic oil that is closed, produce suitable compensator or trimmer pressure and act on the piston 6 oil extraction sides, resist mutually with the inertial force of piston.Hydraulic jack begins to enter buffer status, along with piston rod 3 continues to regain, piston 6 continues to move right, second cushion collar, 11 relative piston rods 3 slide left, and the circulation area of the throttling oil duct 301b between second cushion collar 11 and the piston rod 3 diminishes gradually, and the oil extraction flow diminishes, the compensator or trimmer pressure that rodless cavity produces acts on the piston 6 oil extraction sides to be increased gradually, piston 6 speed reduce gradually, reach the purpose of retarding braking, realize steady buffer deceleration effect.When piston 6 right sides are adjacent to when shoulder of stopping of rodless cavity end cap 12, piston 6 no longer moves right, and piston rod 3 is retracted to stroke terminal, and whole buffering course finishes.
Please refer in the third embodiment of Figure 12, is the improvement in above-mentioned first kind of embodiment.Difference is: piston rod 3 and second cushion collar, 4 matching parts are set with spacer shell 304, and spacer shell 304 cooperates with cushion collar 4.Offer many circumferential balance oil grooves and the straight line throttling oil groove that has tapering on spacer shell 304 outer surfaces, spacer shell 304 cooperates outer surface to carry out the chromium plating processing with first cushion collar 4, improve hardness and surface quality.
In first kind of embodiment, many circumferential balance oil grooves are directly processed on piston rod 3 with the straight line throttling oil groove that has tapering, because piston rod 3 big footpaths, long stroke, many circumferential balance oil grooves are very high with the straight line throttling oil groove requirement on machining accuracy that has tapering, and processing is difficulty very.In the third embodiment, many of machining high-precision uniform circumferential balance oil grooves are very easy to the straight line throttling oil groove that has tapering on spacer shell 304.
Please refer in the 4th kind of embodiment of Figure 13, it is the improvement in above-mentioned first kind of embodiment, difference is: piston rod 3 comprises piston rod body 3a and buffer shaft 3b, and piston rod body 3a and buffer shaft 3b be by being threaded, and then fixing by screw 15.Buffer shaft 3b cooperates with cushion collar 11, is provided with at buffer shaft 3b tail end to be used for the shaft shoulder spacing to cushion collar 11.Cushion collar 3b length is short, and many of machining high-precision circumferential balance oil grooves are easier to the straight line throttling oil groove ratio that has tapering thereon.Placement between piston rod body 3a and the buffer shaft 3b has multiple choices, for example: mode such as being threaded of this programme, welding, bolt connection.
Above-mentioned embodiment when the hydraulic jack rod chamber need cushion, can only be provided with cushion collar in rod chamber; When the hydraulic jack rodless cavity need cushion, cushion collar can only be set in rodless cavity; When rod chamber and rodless cavity need to cushion simultaneously, cushion collar can be set respectively in rod chamber and rodless cavity.Also two cushion collars or a plurality of cushion collar can be set in a chamber.Design according to actual needs.Many circumferential balance oil grooves and many axially extended throttling oil ducts also can be arranged on the cushion collar internal surface, and the throttling oil duct can be that uniform section is long-pending.
Above-mentioned embodiment can be provided with Returnning spring between cushion collar and the piston, and also Returnning spring not is because cushion collar is to contact with the rod chamber end cap to form sealing under the effect of pressure oil.
The hydraulic jack that provides of the present invention, throttling oil duct can also be arranged on the throttling oil duct on the rod chamber end cap, on the rodless cavity end cap, on the cushion collar and on the piston rod except that above-mentioned embodiment.And a shear deformation is all in protection scope of the present invention.
Hydraulic jack provided by the invention is used for hydraulic buffer system replaces existing oil cylinder, can obtain the embodiment of hydraulic buffer system of the present invention.
Hydraulic jack provided by the invention is used for excavator, can obtains the embodiment of excavator of the present invention.
Hydraulic jack provided by the invention is used for concrete mixer, can obtains the embodiment of concrete mixer of the present invention.The engineering machinery that hydraulic jack provided by the invention can also be used for other type.The engineering machinery that hydraulic jack provided by the invention can also be used for other type.
Though the present invention with preferred embodiment openly as above; but it is not to be used for limiting the present invention; any those skilled in the art without departing from the spirit and scope of the present invention; can make possible change and modification, so protection scope of the present invention should be as the criterion with the scope that claim of the present invention was defined.
Claims (17)
1. hydraulic jack, comprise rod chamber end cap (1), cylinder barrel (2), piston rod (3), piston (6) and rodless cavity end cap (12), described rod chamber end cap (1) is provided with oil duct (B), and described rodless cavity end cap (12) is provided with oil duct (A), it is characterized in that:
Also be provided with at least two throttling oil grooves (301a, 301b), described piston rod (3) is provided with at least two cushion collars, described cushion collar comprises first cushion collar (4) that is positioned at rod chamber and second cushion collar (11) that is positioned at rodless cavity, and described cushion collar (4,11) can endwisely slip along described piston rod (3);
Described first cushion collar (4) is provided with seal face (401), rod chamber end cap (1) is provided with seal face (101), stretch out in the movement process at piston, the first cushion collar end face (401) can contact with the seal face (101) of described rod chamber end cap (1) and form sealing surface, and sealing surface can be expelled to oil duct (B) by throttling oil duct (301a) by the hydraulic oil of piston one side;
Described second cushion collar (11) is provided with seal face (111), described rodless cavity end cap (12) is provided with seal face (121), in the piston-retraction movement process, the described second cushion collar end face (121) can contact with the seal face (121) of described rodless cavity end cap (12) and form sealing, and sealing surface can be expelled to oil duct (A) by throttling oil duct (301b) by the hydraulic oil of piston one side;
(301a 301b) is arranged on throttling oil groove on described piston rod (3) outer surface to described throttling oil duct vertically;
When described piston rod (3) when extending out to stroke terminal, described first cushion collar (4) is from its terminal point (L1) at regular intervals that slides towards described piston (6) direction; When described piston rod (3) when being retracted to stroke terminal, described second cushion collar (11) is from its terminal point (L2) at regular intervals that slides towards described piston (6) direction.
2. hydraulic jack according to claim 1 is characterized in that, (301a, 301b) straight line is arranged on throttling oil groove on described piston rod (3) outer surface to described throttling oil duct vertically.
3. hydraulic jack according to claim 1, it is characterized in that: when the seal face (401) of described first cushion collar (4) contacts with the seal face (101) of described rod chamber end cap (1) when forming sealing surface, the pressure oil in the rod chamber to the axial action area of described first cushion collar (4) greater than the axial action area of the hydraulic oil in the described oil channel (B) to described first cushion collar (4).
4. hydraulic jack according to claim 1, it is characterized in that: when the seal face (111) of described second cushion collar (11) contacts with the seal face (121) of described rodless cavity end cap (12) when forming sealing, the pressure oil in the rodless cavity to the axial action area of described second cushion collar (11) greater than the axial action area of the pressure oil in the described oil channel (A) to described second cushion collar (11).
5. hydraulic jack according to claim 1 is characterized in that: the seal face (401) of described first cushion collar (4) contacts with the seal face (101) of described rod chamber end cap (1) and forms face seal or linear sealing.
6. hydraulic jack according to claim 1 is characterized in that, the seal face (111) of described second cushion collar (11) contacts with the seal face (121) of described rodless cavity end cap (12) and forms face seal or linear sealing.
7. according to any described hydraulic jack of claim 1 to 6, it is characterized in that go up to described piston (6) direction at described piston rod (3) when described cushion collar (4,11) and slide, (301a, 301b) cross-section area is along with diminishing for described throttling oil duct.
8. according to any described hydraulic jack of claim 1 to 6, it is characterized in that, be provided with in described cylinder barrel (2) cavity and be used for the elastic element (5,7) that described cushion collar (4,11) resets.
9. according to any described hydraulic jack of claim 1 to 6, it is characterized in that described piston rod (3) is provided with one or many circumferential balance oil grooves (302a, 302b) with the matching surface of described cushion collar (4,11); The cross section of this balance oil groove (302a, 302b) can be V-type, U type or square or other section forms.
10. according to any described hydraulic jack of claim 1 to 6, it is characterized in that described throttling oil duct (301a, 301b) is arranged on the throttling inclined-plane of described cushion collar (4,11) and described piston rod (3) sliding area for axial straight line.
11. according to any described hydraulic jack of claim 1 to 6, it is characterized in that, described piston rod (3) comprises piston rod body and spacer shell (304), described spacer shell (304) is sleeved on the described piston rod body, described cushion collar (4,11) is enclosed within on the described spacer shell (304), and described throttling oil duct (301a, 301b) is arranged on the described spacer shell (304).
12. according to any described hydraulic jack of claim 1 to 6, it is characterized in that, described piston rod (3) comprises piston rod body (3a) and buffer shaft (3b), described piston rod body (3a) and described buffer shaft (3b) interconnect, described second cushion collar (11) is arranged on the described buffer shaft (3b), and described throttling oil duct (301b) is arranged on the described buffer shaft (3b).
13., it is characterized in that described piston rod is provided with the spacing shaft shoulder of cushion collar (4) according to any described hydraulic jack of claim 1 to 6.
14., it is characterized in that the end that described piston rod is positioned at rodless cavity is provided with the only shoulder spacing to cushion collar (11) according to any described hydraulic jack of claim 1 to 6.
15. a hydraulic buffer system is characterized in that, comprises any described hydraulic jack of claim 1 to 14.
16. an excavator is characterized in that comprising any described hydraulic jack of claim 1 to 14.
17. a concrete mixer is characterized in that comprising any described hydraulic jack of claim 1 to 14.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101027313A CN102155457B (en) | 2010-07-23 | 2010-07-23 | Hydraulic oil cylinder, hydraulic buffering system, excavator and concrete pump truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101027313A CN102155457B (en) | 2010-07-23 | 2010-07-23 | Hydraulic oil cylinder, hydraulic buffering system, excavator and concrete pump truck |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010102351381A Division CN102108991B (en) | 2010-07-23 | 2010-07-23 | Hydraulic cylinder, hydraulic buffer system, excavator and concrete pump truck |
Publications (2)
| Publication Number | Publication Date |
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| CN102155457A true CN102155457A (en) | 2011-08-17 |
| CN102155457B CN102155457B (en) | 2012-07-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2011101027313A Active CN102155457B (en) | 2010-07-23 | 2010-07-23 | Hydraulic oil cylinder, hydraulic buffering system, excavator and concrete pump truck |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102705294A (en) * | 2012-06-26 | 2012-10-03 | 上海三一重机有限公司 | High-pressure cylinder and excavator comprising same |
| CN104074836A (en) * | 2014-06-30 | 2014-10-01 | 南京蒙福液压机械有限公司 | High speed hydraulic cylinder buffer mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3999463A (en) * | 1975-02-27 | 1976-12-28 | Componetrol, Inc. | Fluid motor construction |
| CN2746170Y (en) * | 2004-11-12 | 2005-12-14 | 陆平 | Hydraulic bounce cylinder |
| EP1744062A2 (en) * | 2005-07-14 | 2007-01-17 | Norgren GmbH | Actuator with dampening at the end of stroke |
| CN201170229Y (en) * | 2008-03-07 | 2008-12-24 | 汪立平 | Buffering high pressure oil cylinder |
| CN201412408Y (en) * | 2009-06-17 | 2010-02-24 | 江苏恒立高压油缸有限公司 | Floating type buffering hydro cylinder |
-
2010
- 2010-07-23 CN CN2011101027313A patent/CN102155457B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3999463A (en) * | 1975-02-27 | 1976-12-28 | Componetrol, Inc. | Fluid motor construction |
| CN2746170Y (en) * | 2004-11-12 | 2005-12-14 | 陆平 | Hydraulic bounce cylinder |
| EP1744062A2 (en) * | 2005-07-14 | 2007-01-17 | Norgren GmbH | Actuator with dampening at the end of stroke |
| CN201170229Y (en) * | 2008-03-07 | 2008-12-24 | 汪立平 | Buffering high pressure oil cylinder |
| CN201412408Y (en) * | 2009-06-17 | 2010-02-24 | 江苏恒立高压油缸有限公司 | Floating type buffering hydro cylinder |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102705294A (en) * | 2012-06-26 | 2012-10-03 | 上海三一重机有限公司 | High-pressure cylinder and excavator comprising same |
| CN102705294B (en) * | 2012-06-26 | 2016-01-20 | 上海三一重机有限公司 | A kind of high-voltage oil cylinder and comprise the excavator of this oil cylinder |
| CN104074836A (en) * | 2014-06-30 | 2014-10-01 | 南京蒙福液压机械有限公司 | High speed hydraulic cylinder buffer mechanism |
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| Publication number | Publication date |
|---|---|
| CN102155457B (en) | 2012-07-18 |
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