CN103765018B - Fluid-pressure cylinder - Google Patents
Fluid-pressure cylinder Download PDFInfo
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- CN103765018B CN103765018B CN201280042046.9A CN201280042046A CN103765018B CN 103765018 B CN103765018 B CN 103765018B CN 201280042046 A CN201280042046 A CN 201280042046A CN 103765018 B CN103765018 B CN 103765018B
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- piston rod
- cylinder
- bypass
- buffer
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
- F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position
Abstract
Fluid-pressure cylinder be included in piston rod relative to the damping mechanism making piston rod slow down near the stroke end of cylinder barrel.Damping mechanism comprises: buffering bearing, and it is located at piston rod; Buffer cylinder face, buffering bearing is expert near Cheng Duan and is entered this buffer cylinder face; Buffer gap, it divides and is formed between buffer cylinder face and buffering bearing, and for carrying out throttling to the flowing of working fluid; Bypass path, it is for guiding the working fluid in bypass buffer gap; And damper, it is installed on bypass path; Be formed with throttle orifice at damper, this throttle orifice is used for carrying out throttling to the flowing of the working fluid by bypass path.
Description
Technical field
The present invention relates to the fluid-pressure cylinder near a kind of stroke end of the piston rod in cylinder barrel, piston rod being slowed down.
Background technique
The fluid-pressure cylinder (oil hydraulic cylinder) being applied to hydraulic shovel etc. comprises damping mechanism piston rod being slowed down by producing compensator or trimmer pressure near the stroke end of piston rod.
JP8-61311A and JP11-230117A discloses a kind of damping mechanism, and this damping mechanism comprises buffering bearing, and this buffering bearing is for dividing the buffer gap being formed in and making working fluid pass through when piston rod is come near stroke end.The buffer sealing part (Sealing) of the function had as one-way valve is being installed by the inner side of the buffering bearing of floating support.
If piston rod is come near stroke end, then cushion bearing and enter the inner side of cylinder cap and divide formation buffer gap.Thus, working fluid respectively by this buffer gap and buffer sealing part gap (throttling hole slot) and flow out, therefore, produce compensator or trimmer pressure because of the resistance of the flowing of working fluid, thus piston rod slowed down.
Summary of the invention
But, in above-mentioned damping mechanism in the past, owing to being provided with the special buffer sealing part corresponding with specification in the inner side of buffering bearing, therefore, cause the cost increase of product and deviation may be produced due to the size deviation of the gap of buffer sealing part (throttling hole slot) etc. on shock-absorbing capacity.
In addition, owing to being formed with the buffer sealing part groove for holding buffer sealing part in the periphery of piston rod, therefore, need to carry out fluting processing to piston rod.
The object of this invention is to provide a kind of fluid-pressure cylinder not using buffer sealing part just can obtain predetermined compensator or trimmer pressure.
According to certain mode of execution of the present invention, provide a kind of fluid-pressure cylinder, this fluid-pressure cylinder be included in piston rod relative to the damping mechanism making piston rod slow down near the stroke end of cylinder barrel, damping mechanism comprises: buffering bearing, it is located at piston rod; Buffer cylinder face, buffering bearing is expert near Cheng Duan and is entered this buffer cylinder face; Buffer gap, it divides and is formed between buffer cylinder face and buffering bearing, and for carrying out throttling to the flowing of working fluid; Bypass path, it is for guiding the working fluid in bypass buffer gap; And damper, it is installed on bypass path; Be formed with throttle orifice at damper, this throttle orifice carries out throttling to the flowing of the working fluid by bypass path.
Embodiments of the present invention, advantage of the present invention is explained referring to accompanying drawing.
Accompanying drawing explanation
Fig. 1 is the sectional view of the oil hydraulic cylinder of embodiments of the present invention.
Fig. 2 A is the sectional view of the oil hydraulic cylinder after a part of Fig. 1 being amplified.
Fig. 2 B is the sectional view in the A-A cross section representing Fig. 2 A.
Fig. 3 is the sectional view of the oil hydraulic cylinder of state when representing elongation work.
Fig. 4 is the sectional view of the oil hydraulic cylinder of state when representing contraction work.
Embodiment
Below, with reference to the accompanying drawings embodiments of the present invention are described.
Fig. 1 is the sectional view of the oil hydraulic cylinder 1 of embodiments of the present invention.Oil hydraulic cylinder 1 is such as used as the dipper cylinder of hydraulic shovel, by making oil hydraulic cylinder 1 carry out flexible work, the arm of hydraulic shovel is rotated.
Oil hydraulic cylinder (fluid-pressure cylinder) 1 comprises: the cylinder barrel 10 of tubular; Piston 20, bar room 2 and end room 3 demarcate by it in cylinder barrel 10; And piston rod 30, it is linked to piston 20.
Bar room 2 and end room 3 are communicated in not shown hydraulic power (working fluid pressure source), utilize the working hydraulic pressure (working fluid pressure) guided from this hydraulic power to make piston rod 30 move up in central axis O side and carry out flexible work.
In addition, such as water-soluble replacement liquid etc. can also be used to replace oil and as working fluid.
Be provided with cylindric cylinder cap 40 at the opening end of cylinder barrel 10, piston rod 30 runs through this cylinder cap 40 in the mode that can slide.Screw togather and fastening cylinder cap 40 with the inner circumferential screw section (internal thread) 12 of cylinder barrel 10 by making the screw section, periphery (outside thread) 41 of cylinder cap 40.
Cylinder cap 40 has the cylinder cap embedding part 42 of the cylindrical shape being embedded in cylinder body inner peripheral surface 11.At the peripheral part of cylinder cap embedding part 42, O type circle 9 and guard circle (Japanese: バ ッ Network ア ッ プ リ Application グ) 19 are installed.
Bearing 55, secondary Sealing 56, primary seal 57, dust seal 58 is separately installed with, bar outer circumferential face 31 sliding contact of these bearings 55, secondary sealing 56, primary seal 57, dust seal 58 and piston rod 30 in the inner peripheral portion of cylinder cap 40.By bearing 55 and bar outer circumferential face 31 sliding contact, piston rod 30 is supported in the mode moved in parallel with the central axis O direction of cylinder barrel 10.
Be formed with supply and discharge mouth 43 at cylinder cap 40, utilize this supply and discharge mouth 43 to divide and form supply and discharge path 5.Supply and discharge path 5 via be connected to cylinder barrel 10 pipe arrangement mouth 17 not shown hydraulic piping and be communicated with hydraulic power.
The cylinder cap inner peripheral surface 44 of cylinder planar is formed in the inner circumferential of cylinder cap 40.One end of supply and discharge mouth 43, at this cylinder cap inner peripheral surface 44 opening, divides and forms supply and discharge path 5 between cylinder cap inner peripheral surface 44 and bar outer circumferential face 31.
In the inner side of cylinder barrel 10, holder 23 is installed.It is circular that holder 23 is formed as centered by central axis O.Holder 23 is embedded in cylinder body inner peripheral surface 11 side by side with the cylinder cap embedding part 42 of cylinder cap 40.At the peripheral part of holder 23, O type circle 28 and guard circle 18 are installed.
Holder 23 has buffer cylinder face 24 as inner circumferential surface.Buffer cylinder face 24 is formed as the cylinder planar centered by central axis O.
By its tapering, periphery, and the upper-end surface of this holder chimeric with the conical surface 13 of cylinder body inner peripheral surface 11 abuts against with the cylinder cap end face 45 of the lower end being formed at cylinder cap 40 and fixes holder 23.
In addition, about the fixation method of holder 23, be not limited thereto, such as, also can be fixed on cylinder cap 40 by not shown bolt.In this case, the conical surface 13 need not be formed at the internal surface of cylinder barrel 10.In addition, holder 23 can also be integrally formed at cylinder cap 40.
In FIG, when the oil hydraulic cylinder 1 of piston rod 30 movement downwards shrinks work, the pressurized operation oil that self-hydraulic source is supplied by hydraulic piping flows into bar room 2 by supply and discharge path 5.
On the other hand, in FIG, when the oil hydraulic cylinder 1 that piston rod 30 is moved upward stretches work, in the trip process, the working oil of bar room 2 is by supply and discharge path 5, supply and discharge mouth 43, hydraulic piping and flowing out to hydraulic power.
Oil hydraulic cylinder 1 is provided with damping mechanism 6, and this damping mechanism 6 makes piston rod 30 slow down when piston rod 30 is come near stroke end.Fig. 1 represents that piston rod 30 is positioned at more forward than stroke end and is the state near stroke end.
Damping mechanism 6 comprises the buffering bearing 60 of the cylindrical shape being installed on piston rod 30.If piston rod 30 is come near stroke end, then cushion bearing 60 and enter the inner side of holder 23, thus divides between buffering bearing 60 and holder 23 form buffer gap 4(reference Fig. 3).Utilize this buffer gap 4, resistance is applied to the flowing of the working oil flowed out by supply and discharge path 5 from bar room 2, makes the pressure (hereinafter referred to as compensator or trimmer pressure) of bar room 2 increase.If compensator or trimmer pressure rises, then piston rod 30 is made to slow down.
Buffering bearing 60 has bearing outer circumferential face 61 as its outer circumferential face.Bearing outer circumferential face 61 is formed as the cylinder planar centered by central axis O.The external diameter of bearing outer circumferential face 61 is formed as being greater than the external diameter of bar outer circumferential face 31 and is less than the internal diameter in buffer cylinder face 24.Buffer gap 4 divides and is formed between bearing outer circumferential face 61 and buffer cylinder face 24.
The circle of contact portion 62(otch cut bearing outer circumferential face 61 local is formed) at buffering bearing 60.That is, circle of contact portion 62 is for being located at the recess of bearing outer circumferential face 61.The width in circle of contact portion 62 is formed as more going to the below of Fig. 1 and becoming narrower.Thus, in buffer gap 4, utilize circle of contact portion 62 to divide the flow path cross sectional area formed and reduce gradually accordingly near stroke end with piston rod 30.The clearance (gap width) of buffer gap 4 and the shape in circle of contact portion 62 can the deceleration characteristic required by damping mechanism 6 set.
Damping mechanism 6 comprises: bypass path 50, and it is for guiding the working oil in bypass buffer gap 4; And damper (adjustment screw) 63, it is installed on bypass path 50; The throttle orifice 64 flowing of the working oil by bypass path 50 being carried out to throttling is formed at damper 63.
Bypass path 50 utilizes the bypass through hole 25 running through holder 23 to divide and is formed.Bypass through hole 25 is extended substantially in parallel with central axis O, at the upper and lower end face of holder 23 difference opening.
Fig. 2 A is the sectional view after a part of Fig. 1 being amplified, and Fig. 2 B is the sectional view in the A-A cross section representing Fig. 2 A.
Be formed with the holder recess 26 of the upper-end surface depression of self-insurance gripping member 23 in the upper-end surface of holder 23, the upper end of bypass through hole 25 is at holder recess 26 opening.In addition, being not limited thereto, also can be do not arrange holder recess 26 and make the upper end of bypass through hole 25 in the structure of the upper-end surface opening of holder 23.
Be formed with the cylinder cap end face 45 orthogonal with central axis O in the lower end of cylinder cap 40, the upper-end surface of holder 23 is connected to cylinder cap end face 45.
The bypass recess 46 in the discoid depression centered by central axis O is formed at cylinder cap end face 45.Bypass recess 46 is formed in the mode stood facing each other mutually with the holder recess 26 of holder 23 and the opening end of bypass through hole 25, divides and form bypass path 50 between the opening end and bypass recess 46 of holder recess 26 and bypass through hole 25.
When oil hydraulic cylinder 1 stretches work, if piston rod 30 is come near stroke end, then as shown in arrow in Fig. 2 A, the working oil of bar room 2 is by bypass path 50, supply and discharge path 5 and flowing out to hydraulic power.
Notch 29 is formed in the lower end surface of holder 23.Thus, under the state that oil hydraulic cylinder 1 at utmost extends, the upper-end surface 22 of piston 20 abuts against with the lower end surface of holder 23.Now, buffer gap 4 is communicated with bar room 2 via notch 29 with bypass path 50.
Throttle orifice 64 applies resistance to the working oil of flowing in bypass path 50.Together therewith, the compensator or trimmer pressure of bar room 2 rises, and piston rod 30 is slowed down.The opening diameter of throttle orifice 64 and path-length can deceleration characteristics required by damping mechanism 6 and setting.
In bypass path 50, the working oil that have passed throttle orifice 64 flows out to the gap between the holder recess 26 of holder 23 and the bypass recess 46 of cylinder cap 40, encounters the internal face of bypass recess 46 and turns to towards the direction of central axis O.Thereby, it is possible to prevent the jet flow of the working oil because have passed throttle orifice 64 and cause producing noise.
Screw section, periphery (outside thread) 66 is formed in the periphery of the damper 63 of cylindrical shape.On the other hand, inner circumferential screw section 27 is formed with at the bypass through hole 25 of holder 23.By being screwed togather with the inner circumferential screw section 27 of holder 23 screw section, periphery 66 of damper 63, damper 63 is installed.Because holder 23 is arranged independent of cylinder cap 40, therefore, it is possible to easily carry out machining to bypass through hole 25, and the cost seeking product reduces.
Throttle orifice 64 and hexagon ring 65 is formed side by side in the inner circumferential of damper 63.Damper 63 utilizes the instrument (not shown) being sticked in hexagon ring 65 to be fastened and fixed in inner circumferential screw section 27.
In addition, be not limited thereto, damper 63 also can be the structure of being undertaken by the bypass through hole 25 of press-in holder 23 installing.In addition, damper 63 is installed on the upper end portion of the bypass through hole 25 of holder 23, but is not limited thereto, and also can be installed on the underpart of bypass through hole 25.
In addition, such structure can also be set to: divide at holder 23 through hole forming bypass path 50 and be formed as extending along the direction roughly orthogonal with central axis O, damper 63 is installed on this through hole.In this case, the opening end of through hole stands facing each other with cylinder body inner peripheral surface 11 phase, utilizes cylinder body inner peripheral surface 11 by locking for damper 63 for coming off.
Be formed as being less than the length R2 from central axis O to the peripheral end of damper 63 from length (radius of curvature) R1 of central axis O to dividing the periphery wall portion of the bypass recess 46 forming cylinder cap 40.As shown in Figure 2 B, a part for the cylinder cap end face 45 of cylinder cap 40 stands facing each other mutually with a part for damper 63.
Thus, even if the damper be screwed with the inner circumferential screw section 27 of holder 23 63 loosens and gives prominence to upward from bypass through hole 25, a part for damper 63 also can abut against with the cylinder cap end face 45 of cylinder cap 40, thus can prevent damper 63 from giving prominence to upward further.In this condition, bypass through hole 25 is connected with bypass recess 46.Thereby, it is possible to prevent the bypass through hole 25 of damper 63 self-insurance gripping member 23 from coming off, and, because bypass path 50 is not closed, therefore, it is possible to maintain the work of damping mechanism 6.
Buffering bearing 60 with in the radial direction and the mode between piston rod 30 with bearing inner circumferential gap 7 be embedded in piston rod 30, and with can relative to the mode of piston rod 30 movement by floating support.Between the inner peripheral surface 67 that the division of bearing inner circumferential gap 7 is formed in buffering bearing 60 and the end outer circumferential face 33 of piston rod 30.
Buffering bearing 60 with on central axis O direction and the mode between piston rod 30 with gap 8 be installed on piston rod 30.Under the state of upper-end surface 22 that the lower end surface of buffering bearing 60 is connected to piston 20, between the upper-end surface 68 that gap 8 division is formed in buffering bearing 60 and the circular step portion 32 of piston rod 30.
Notch 69 is formed in the lower end surface of buffering bearing 60.Under the state of upper-end surface 22 that the lower end surface of buffering bearing 60 is connected to piston 20, bearing inner circumferential gap 7 is communicated with bar room 2 by notch 69.
Fig. 3 represents that oil hydraulic cylinder 1 that piston rod 30 is moved upward as shown in hollow arrow is when the work of stretching, extension and be the sectional view of the state of piston rod 30 when coming near stroke end.
If piston rod 30 is come near stroke end, then the inner side by making buffering bearing 60 enter holder 23, thus divide and form buffer gap 4 between buffering bearing 60 and holder 23.
Buffer gap 4 applies resistance to the flowing of the working oil flowed out to supply and discharge path 5 from bar room 2, and the compensator or trimmer pressure of bar room 2 rises.Together therewith, buffering bearing 60 is pressed upward, and the buffering upper-end surface of bearing 60 and the circular step portion 32 of piston rod 30 abut against, and gap 8 is closed and closes between bearing inner circumferential gap 7 and supply and discharge path 5.
Thus, as shown by the arrows in Figure 3, the working oil of bar room 2 flows out from supply and discharge path 5 respectively by buffer gap 4 and bypass path 50.The throttle orifice 64 of buffer gap 4 and bypass path 50 applies resistance to the flowing of the working oil flowed out from bar room 2, by making the compensator or trimmer pressure of bar room 2 rise, piston rod 30 is slowed down.
Fig. 4 represents that the oil hydraulic cylinder 1 of piston rod 30 movement downwards as shown in hollow arrow is when the work of contraction and be the sectional view of state of piston rod 30 when coming near stroke end.
If pressurized operation oil self-hydraulic source is fed into supply and discharge path 5, then cushion bearing 60 to be pressed downwards, the circular step portion 32 of piston rod 30 is left in the upper-end surface of buffering bearing 60, and divide and form gap 8 between buffering bearing 60 and piston rod 30, thus make between bearing inner circumferential gap 7 and supply and discharge path 5 open-minded.
Thus, as shown by the arrows in Figure 4, be fed into the pressurized operation oil of supply and discharge path 5 by gap 8, bearing inner circumferential gap 7, notch 69 and flow into bar room 2, and flow into bar room 2 respectively by buffer gap 4 and bypass path 50.Because working oil so flows into bar room 2 via three streams, therefore, piston rod 30 promptly moves to shrinkage direction.
So, cushion bearing 60 to play near stroke end and open the function of the one-way valve in bearing inner circumferential gap 7 as when closing bearing inner circumferential gap 7, another aspect in contraction work when the work of elongation.
Below, the main idea of present embodiment and effect, effect are described.
The oil hydraulic cylinder 1 of present embodiment comprises damping mechanism 6, and this damping mechanism 6 makes piston rod 30 slow down at piston rod 30 relative near the stroke end of cylinder barrel 10.Damping mechanism 6 comprises: buffering bearing 60, and it is located at piston rod 30; Buffer cylinder face 24, buffering bearing 60 enters this buffer cylinder face 24 near stroke end; Buffer gap 4, its divide be formed in this buffer cylinder face 24 and buffering bearing 60 between and throttling is carried out to the flowing of working fluid; Bypass path 50, it walks around the working fluid of this buffer gap 4 for guiding; And damper 63, it is installed on this bypass path 50.The throttle orifice 64 flowing of the working fluid by bypass path 50 being carried out to throttling is formed at damper 63.
Thus, by changing the shape, the size that are formed at the throttle orifice 64 of damper 63, the resistance that the flowing of the working oil by bypass path 50 is applied can be adjusted, predetermined compensator or trimmer pressure can be obtained.
Owing to being formed with throttle orifice 64 at the damper 63 being installed on bypass path 50, therefore, can will divide holder 23 sharing between the product of different size forming bypass path 50, and can when not increasing the production code member of holder 23 by means of only the corresponding different specification of change damper 63.In addition, formed compared with the situation of throttle orifice with dividing the holder 23 forming bypass path 50, the machining accuracy of throttle orifice 64 can be improved, the deviation of shock-absorbing capacity can be suppressed.
Due to buffer sealing part need not be installed in the inner side of buffering bearing 60 as device in the past, therefore, it is possible to the cost seeking product declines, and the deviation of the shock-absorbing capacity relevant to buffer sealing part can be eliminated.
Due to the buffer sealing part groove installed for buffer sealing part need not be formed in the periphery of piston rod 30 as device in the past, therefore, it is possible to improve the intensity of piston rod 30.
In the present embodiment, damping mechanism 6 comprises: cylinder cap 40, its mode supporting piston bar 30 that can slide to make piston rod 30; And the holder 23 of ring-type, itself and cylinder cap 40 are installed on the inner side of cylinder barrel 10 side by side.Holder 23 has: buffer cylinder face 24; And bypass through hole 25, it divides a part for formation bypass path 50 and is provided with damper 63.Cylinder cap 40 has: cylinder cap end face 45, and it stands facing each other mutually with the opening end of bypass through hole 25; And bypass recess 46, its depression is arranged at cylinder cap end face 45 and divides the part forming bypass path 50; Be set to the length R1 divided the periphery wall portion forming bypass recess 46 the length R2 of central axis O to the peripheral end of damper 63 be less than from piston rod 30 from central axis O, therefore, it is possible to by locking for damper 63 for can not come off from bypass through hole 25.
Thereby, it is possible to prevent the bypass through hole 25 of damper 63 self-insurance gripping member 23 from coming off, and, because bypass path 50 is not closed, therefore, it is possible to maintain the work of damping mechanism 6.
In addition, because the holder 23 being provided with damper 63 is formed independent of cylinder cap 40, therefore, by changing the holder 23 corresponding with required deceleration characteristic and damper 63, easily shock-absorbing capacity can be adjusted.
In the present embodiment, the cylinder cap end face 45 stood facing each other with bypass through hole 25 phase is formed at cylinder cap 40.
Thus, by adding holder 23 when not changing the basic shape of cylinder cap 40, damping mechanism 6 can be formed, the cost increase of product can be suppressed.
In the present embodiment, damping mechanism 6 comprises: cylinder cap 40, its mode supporting piston bar 30 that can slide to make piston rod 30; And supply and discharge path 5, it divides and to be formed between piston rod 30 and cylinder cap 40 and for supply and discharge working fluid.Buffering bearing 60 is to have the mode floating support in bearing inner circumferential gap 7 in piston rod 30 between piston rod 30.When cushioning bearing 60 and entering the work in buffer cylinder face 24, be closed between bearing inner circumferential gap 7 and supply and discharge path 5, on the other hand, open-minded between bearing inner circumferential gap 7 and supply and discharge path 5 when cushioning the work that bearing 60 exits from buffer cylinder face 24.
Thus, because buffering bearing 60 plays function, therefore, it is possible to promptly make piston rod 30 move when fluid-pressure cylinder 1 drives as by the one-way valve opened between bearing inner circumferential gap 7 and supply and discharge path 5, close.
Above, describe embodiments of the present invention, but above-mentioned mode of execution is only the part application examples of the present invention, its aim does not also lie in concrete structure technical scope of the present invention being defined in above-mentioned mode of execution.
Such as, multiple annular slot (maze trough) can be formed at the inner peripheral surface 67 of buffering bearing 60 and the end outer circumferential face 33 of piston rod 30 dividing formation bearing inner circumferential gap 7.Thereby, it is possible to apply resistance to the working fluid of flowing in bearing inner circumferential gap 7 and buffering bearing 60 remained on on the same axis of piston rod 30.
In addition, in the above-described embodiment, situation piston rod being slowed down when the elongation work of oil hydraulic cylinder 1 exemplified with damping mechanism, also can be set to the structure that damping mechanism makes piston rod slow down when the contraction work of oil hydraulic cylinder 1 near the stroke end of piston rod.
The application is based on the Japanese Patent Application 2011-193792 CLAIM OF PRIORITY of on September 6th, 2011 to Japanese Patent Office application, and the full content of this application is by referring to being programmed in this specification.
Claims (3)
1. a fluid-pressure cylinder, its be included in piston rod relative to the damping mechanism making piston rod slow down near the stroke end of cylinder barrel, above-mentioned damping mechanism comprises:
Buffering bearing, it is located at above-mentioned piston rod;
Buffer cylinder face, above-mentioned buffering bearing is expert near Cheng Duan and is entered this buffer cylinder face;
Buffer gap, its division is formed between above-mentioned buffer cylinder face and above-mentioned buffering bearing, and for carrying out throttling to the flowing of working fluid;
Bypass path, it walks around the working fluid of above-mentioned buffer gap for guiding; And
Damper, it is installed on above-mentioned bypass path in the mode of screw threads for fastening or press-in;
Be formed with throttle orifice at above-mentioned damper, this throttle orifice carries out throttling to the flowing of the working fluid by above-mentioned bypass path.
2. fluid-pressure cylinder according to claim 1, wherein,
Above-mentioned damping mechanism comprises:
Cylinder cap, it supports this piston rod in the mode enabling above-mentioned piston rod and slide; And
The holder of ring-type, itself and above-mentioned cylinder cap are installed on the inner side of above-mentioned cylinder barrel side by side;
Above-mentioned holder has: above-mentioned buffer cylinder face; And bypass through hole, it is provided with above-mentioned damper, and this bypass through hole divides the part forming above-mentioned bypass path;
Above-mentioned cylinder cap has: cylinder cap end face, and it stands facing each other mutually with the opening end of above-mentioned bypass through hole; And bypass recess, it is formed at above-mentioned cylinder cap end face, and divides the part forming above-mentioned bypass path;
Be formed as being less than the length of central axis to the peripheral end of above-mentioned damper from above-mentioned piston rod to the length divided the periphery wall portion forming above-mentioned bypass recess from the central axis of above-mentioned piston rod.
3. fluid-pressure cylinder according to claim 1, wherein,
Above-mentioned damping mechanism comprises:
Cylinder cap, it supports this piston rod in the mode enabling above-mentioned piston rod and slide; And
Supply and discharge path, its division is formed between above-mentioned piston rod and above-mentioned cylinder cap, and for supply and discharge working fluid;
Above-mentioned buffering bearing there is the mode floating support in bearing inner circumferential gap between this buffering bearing and above-mentioned piston rod in above-mentioned piston rod,
When above-mentioned buffering bearing enters the work in above-mentioned buffer cylinder face, close between above-mentioned bearing inner circumferential gap and above-mentioned supply and discharge path, when the work that above-mentioned buffering bearing exits from above-mentioned buffer cylinder face, open-minded between above-mentioned bearing inner circumferential gap and above-mentioned supply and discharge path.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-193792 | 2011-09-06 | ||
| JP2011193792A JP5789456B2 (en) | 2011-09-06 | 2011-09-06 | Fluid pressure cylinder |
| PCT/JP2012/071271 WO2013035540A1 (en) | 2011-09-06 | 2012-08-23 | Hydraulic pressure cylinder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103765018A CN103765018A (en) | 2014-04-30 |
| CN103765018B true CN103765018B (en) | 2015-11-25 |
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ID=47831990
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280042046.9A Active CN103765018B (en) | 2011-09-06 | 2012-08-23 | Fluid-pressure cylinder |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5789456B2 (en) |
| KR (1) | KR101596176B1 (en) |
| CN (1) | CN103765018B (en) |
| WO (1) | WO2013035540A1 (en) |
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|---|---|---|---|---|
| JP6546746B2 (en) * | 2015-02-10 | 2019-07-17 | Ｋｙｂ株式会社 | Fluid pressure cylinder |
| JP6097799B2 (en) * | 2015-08-25 | 2017-03-15 | Ｋｙｂ株式会社 | Fluid pressure cylinder |
| JP6581457B2 (en) * | 2015-10-01 | 2019-09-25 | Ｋｙｂ−Ｙｓ株式会社 | Fluid pressure cylinder |
| JP6255440B2 (en) * | 2016-03-31 | 2017-12-27 | Ｋｙｂ株式会社 | Fluid pressure cylinder |
| US11067104B1 (en) | 2020-11-16 | 2021-07-20 | Caterpillar Inc. | Integrated cylinder piston and bearing as a hydraulic cushion |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1182425A (en) * | 1997-09-17 | 1999-03-26 | Hitachi Constr Mach Co Ltd | Cushioning structure of hydraulic cylinder |
| JPH11230117A (en) * | 1998-02-18 | 1999-08-27 | Kayaba Ind Co Ltd | Hydraulic cylinder |
| JP2000120614A (en) * | 1998-08-12 | 2000-04-25 | Hitachi Constr Mach Co Ltd | Floating type cushion device of hydraulic cylinder |
| JP3723709B2 (en) * | 1999-12-27 | 2005-12-07 | 株式会社アイチコーポレーション | Hydraulic cylinder operation control device |
| EP2317154A1 (en) * | 2009-10-28 | 2011-05-04 | Volvo Construction Equipment Holding Sweden AB | Hydraulic cylinder cushion device with check ring |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6059804U (en) * | 1983-09-30 | 1985-04-25 | 小松ゼノア株式会社 | Hydraulic cylinder shock absorber |
-
2011
- 2011-09-06 JP JP2011193792A patent/JP5789456B2/en active Active
-
2012
- 2012-08-23 WO PCT/JP2012/071271 patent/WO2013035540A1/en active Application Filing
- 2012-08-23 CN CN201280042046.9A patent/CN103765018B/en active Active
- 2012-08-23 KR KR1020147004376A patent/KR101596176B1/en active IP Right Grant
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1182425A (en) * | 1997-09-17 | 1999-03-26 | Hitachi Constr Mach Co Ltd | Cushioning structure of hydraulic cylinder |
| JPH11230117A (en) * | 1998-02-18 | 1999-08-27 | Kayaba Ind Co Ltd | Hydraulic cylinder |
| JP2000120614A (en) * | 1998-08-12 | 2000-04-25 | Hitachi Constr Mach Co Ltd | Floating type cushion device of hydraulic cylinder |
| JP3723709B2 (en) * | 1999-12-27 | 2005-12-07 | 株式会社アイチコーポレーション | Hydraulic cylinder operation control device |
| EP2317154A1 (en) * | 2009-10-28 | 2011-05-04 | Volvo Construction Equipment Holding Sweden AB | Hydraulic cylinder cushion device with check ring |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103765018A (en) | 2014-04-30 |
| JP5789456B2 (en) | 2015-10-07 |
| WO2013035540A1 (en) | 2013-03-14 |
| JP2013053718A (en) | 2013-03-21 |
| KR101596176B1 (en) | 2016-02-19 |
| KR20140050068A (en) | 2014-04-28 |
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Address after: Tokyo, Japan, Japan Patentee after: KAYABA INDUSTRY CO LTD Address before: Tokyo, Japan, Japan Patentee before: Kayaba Industry Co., Ltd. |